CN103797227B

CN103797227B - Crank-pin including cam, including follower connecting rod, and the explosive motor including crank-pin and connecting rod

Info

Publication number: CN103797227B
Application number: CN201280032160.3A
Authority: CN
Inventors: 拉里·C·威尔金斯
Original assignee: Individual
Current assignee: Individual
Priority date: 2011-05-19
Filing date: 2012-05-16
Publication date: 2017-05-31
Anticipated expiration: 2032-05-16
Also published as: JP6030127B2; EP2710244A4; CN103797227A; US20150122213A1; EP2710244A1; US9016258B2; JP2014517894A; US9080597B2; WO2012158782A1; US20120292906A1

Abstract

A kind of bent axle, it may include the first axle journal and the second axle journal with circular cross section；And crank-pin, the crank-pin extends between the first crank-pin axle journals and the second crank-pin axle journals.The crank-pin may include the first cam, the second cam and the 3rd cam, and it includes respective first cam contour, the second cam contour and the 3rd cam contour, wherein first cam contour, the second cam contour and the 3rd cam contour are different from each other.At least one of first cam contour, the second cam contour and the 3rd cam contour can be configured to influence the stroke of the connecting rod for being couple to the crank-pin.Connecting rod may include the first follower, the second follower and the 3rd follower, and it includes respective first follower surface, the second follower surface and the 3rd follower surface, wherein first follower surface and the second follower surface are different from each other.Explosive motor may include crankshaft-and-connecting-rod, and it is configured to provide relative linear movement between the near-end of crank pin axis and the connecting rod.

Description

Crank-pin including cam, including follower connecting rod, and including crank-pin and connecting rod Explosive motor

Priority request

U.S. Provisional Application No. 61/540,715 filed in this PCT International Patent Application requirement September in 2011 29 days and U.S. Provisional Application No. 61/488 filed in 19 days Mays in 2011, the priority right of No. 067, the two disclose to quote Mode is incorporated herein.

Technical field

This disclosure relates to bent axle, connecting rod and explosive motor.Particularly, this disclosure relates to have improved fuel efficiency And/or the explosive motor of power output.

Background of invention

Fuel cost and the expectation to reducing the undesirable discharge related to the operation of explosive motor higher is changing Enter in the fuel efficiency during operation and generate concern once again.Accordingly, it may be desirable to improve the efficiency of conventional internal combustion engine.

Conventional internal combustion engine includes cylinder block, and it defines the axle journal for receiving bent axle, and one or more cylinders, its Cover the piston for being operatively coupled to bent axle via connecting rod at crank-pin.During routine operation, piston is reciprocal in cylinder Motion so that during the power stroke of explosive motor, the sky in combustion chamber defined by piston, cylinder and cylinder head The burning of gas/fuel mixture forces the piston towards bent axle.As piston is advanced towards bent axle, bent axle is via connecting rod and crank-pin Rotation, so as to the ability related to the burning of air/fuel mixture is converted into mechanical work.

Due to the framework of conventional internal combustion engine, when piston is in meets the position of maximum compression in cylinder（That is, work is worked as Plug away from bent axle it is farthest when combustion chamber be in its minimum capacity）, the footpath extended between the center of bent axle and the center of crank-pin Tend to almost conllinear with pitman shaft to axis（If without conllinear）.In these relative positions, as piston is in the power stroke phase Between be first begin to it towards the motion of bent axle, the very short arm of force is only created between pitman shaft and radial axle（If any）.As a result, most If just by air/fuel mixture in burning the power that is created cannot will be bigger with the length of the arm of force when torque that will convert Equally big torque is delivered to bent axle.Such case may not expect especially because during burning and after burning soon, it is living Power beyond the Great Wall is due to combustion case close to its maximum magnitude.Additionally, as piston is travel downwardly and power along cylinder towards bent axle The length of arm increases, and the value for acting on the power on piston from combustion case dissipates rapidly.Consequently, because on piston The very short arm of force is created during the time of maximum, force between pitman shaft and radial axle, so producing the effect of work(from combustion process Rate is likely less than desired efficiency.

Accordingly, it may be desirable to provide a kind of explosive motor, it has and improves internal combustion engine efficiency during operation Construction.Furthermore, it may be desirable to provide a kind of explosive motor, it has the construction for allowing to customize desired Performance Characteristics.

Brief summary of the invention

In the following description, some aspects and embodiment will be apparent.It should be understood that the aspect and embodiment can Put into practice with its broadest meaning in terms of without these and in the case of one or more features of embodiment.Ying Li Solution, these aspects and embodiment are only exemplary.

An aspect of this disclosure is related to the bent axle of explosive motor.Bent axle may include the first axle journal, and it has and defines The circular cross section of one journal centre, the first axle journal is configured to be rotatably coupled to the cylinder block of explosive motor.Bent axle The second axle journal can also be included, it has the circular cross section for defining the second journal centre, and the second axle journal is configured to rotatable Be couple to the cylinder block of explosive motor, wherein the first journal centre and the second journal centre define North-south crankshaft axis.It is bent Axle can also include defining the crank-pin of longitudinal crank pin axis, and it is configured to be couple to connecting rod, longitudinal crank-pin Diameter parallel is spaced apart in North-south crankshaft axis and with North-south crankshaft axis.Crank-pin may include at least one crank-pin axle journals, The first cam including the first cam contour, including the second cam contour the second cam, and including the 3rd cam contour Three cams.First cam contour, the second cam contour and the 3rd cam contour can be different from each other, and the first cam contour, second At least one of cam contour and the 3rd cam contour are configured to influence the stroke of the connecting rod for being couple to crank-pin.

According on the other hand, the connecting rod of explosive motor may include bar portion and cap, and wherein bar portion and cap is defined by structure Make to receive the elliptical openings of the crank-pin of explosive motor.The first end of elliptical openings can be related to bar portion, and oval Second end of shape opening can be related to cap.Connecting rod can also include that related to the first end of elliptical openings first is servo-actuated Part, second follower related to the first end of elliptical openings, and the related to the second end of elliptical openings the 3rd be servo-actuated Part.First follower may include the first follower surface, and the second follower may include the second follower surface, and first is servo-actuated Part surface and the second follower surface are different from each other.

According to also having on one side, explosive motor may include to define the cylinder block of cylinder, and the bent axle including crank-pin. Wherein bent axle is rotatably coupled to cylinder block and can be rotated along North-south crankshaft axis.Crank-pin can be defined parallel to longitudinal song Axle axis and the longitudinal crank pin axis being spaced apart with North-south crankshaft axis.The engine can also include being configured in gas Reciprocating piston in cylinder, and including connecting rod proximally and distally, wherein the near-end is operatively coupled to crank-pin, and institute It is couple to piston with stating far-end operation.Crank-pin may include at least one crank-pin axle journals, and connecting rod revolves around the crank-pin axle journals Turn；The first cam including the first cam contour, including the second cam contour the second cam, and including the 3rd cam contour 3rd cam.First cam contour, the second cam contour and the 3rd cam contour can be different from each other, and the first cam contour, At least one of two cam contours and the 3rd cam contour can be configured to longitudinal crank pin axis and connecting rod near-end it Between relative linear movement is provided.

According to another aspect, explosive motor may include to define the cylinder block of cylinder, and the bent axle including crank-pin, its Middle bent axle is rotatably coupled to cylinder block, and is rotated along North-south crankshaft axis.Crank-pin can be defined parallel to North-south crankshaft Axis and the longitudinal crank pin axis being spaced apart with North-south crankshaft axis.The engine can also include being configured in cylinder Interior reciprocating piston, and including connecting rod proximally and distally, wherein the near-end is operatively coupled to crank-pin, and it is described It is couple to piston far-end operation.Crank-pin may include at least one crank-pin axle journals, and connecting rod rotates around the crank-pin axle journals； The first cam including the first cam contour, including the second cam contour the second cam, and including the 3rd cam contour Three cams.First cam contour, the second cam contour and the 3rd cam contour are different from each other, and the first cam contour, second convex Wheel at least one of profile and the 3rd cam contour can be configured to provide relative line between near-end of the crank-pin with connecting rod Property motion, cause the distance between longitudinal crank pin axis and piston upper surface as bent axle rotates and change.

According to also having on one side, explosive motor may include to define the cylinder block of cylinder, and the bent axle including crank-pin, Wherein bent axle is rotatably coupled to cylinder block, and is rotated along North-south crankshaft axis.Crank-pin can be defined parallel to longitudinal song Axle axis and relative to longitudinal crank pin axis of a certain distance of North-south crankshaft journal offset.The engine can also include quilt Construction is come reciprocating piston between the stroke endpoint spaced apart that piston stroke is defined in cylinder.The engine may be used also So that including connecting rod, it is included proximally and distally, wherein the near-end is operatively coupled to crank-pin, and far-end operation ground coupling It is connected to piston.Crank-pin may include at least one crank-pin axle journals, and connecting rod rotates around the crank-pin axle journals；Including the first cam First cam of profile, including the second cam contour the second cam, and the 3rd cam including the 3rd cam contour.First is convex Wheel profile, the second cam contour and the 3rd cam contour can be different from each other.North-south crankshaft axis and longitudinal crank pin axis it Between the line that extends can define the longitudinal axis of bent axle.In first cam contour, the second cam contour and the 3rd cam contour extremely Few one can be configured to change the distance between distal end of longitudinal crank pin axis and connecting rod.The engine can be constructed to be made Obtain as bent axle rotates, after piston reaches at least one of stroke endpoint, the row of reverse direction of the piston in cylinder The relative motion entered between longitudinal crank pin axis and the near-end of connecting rod and be delayed by.

According to another aspect, explosive motor may include to define the cylinder block of cylinder, and the bent axle including crank-pin, its Middle bent axle is rotatably received by cylinder block, and is rotated along North-south crankshaft axis.Crank-pin can be defined parallel to North-south crankshaft Axis and relative to longitudinal crank pin axis of a certain distance of North-south crankshaft journal offset.The engine can also include by structure The reciprocating piston in cylinder is made, and including connecting rod proximally and distally, wherein the near-end is operatively coupled to song Handle pin, and the far-end operation be couple to piston.Crank-pin may include at least one crank-pin axle journals, and connecting rod is around the crank Pin journal rotates；The first cam including the first cam contour, including the second cam contour the second cam, it is and convex including the 3rd Take turns the 3rd cam of profile.First cam contour, the second cam contour and the 3rd cam contour are different from each other.In North-south crankshaft axle The line extended between line and longitudinal crank pin axis can define the longitudinal axis of bent axle, wherein the first cam contour, the second cam At least one of profile and the 3rd cam contour be configured to change between longitudinal crank pin axis and the distal end of connecting rod away from From.The engine can be configured to be selectively operable in two patterns, including first mode, wherein longitudinal crank pin The distance between distal end of line and connecting rod changes according to the first strategy of the Angle Position of the longitudinal axis based on bent axle, and second Pattern, wherein the distance between distal end of longitudinal crank pin axis and connecting rod is according to the Angle Position of the longitudinal axis based on bent axle Second strategy and change.First strategy may differ from the second strategy.

According to another aspect, PWTN may include the explosive motor according to any of above aspect, operatively coupling It is connected to the transmission device of engine, and the drive member for being configured to acting.Drive member is operably coupled to transmission device.

According to also having on one side, the vehicles may include the explosive motor according to any of above aspect, operatively coupling It is connected to the transmission device of engine, and the drive member for being configured to acting.Drive member is operably coupled to transmission device.

The extra objects and advantages of the disclosure illustrate part in the following description, or can be by the reality disclosed in practice Apply scheme and study.

In addition to the structure and program that are described above are configured, embodiment may include many other configurations, following article solution The configuration released.It should be understood that being described above and being described below what is be merely exemplary.

Brief description

The accompanying drawing for being incorporated in this description and constituting a part for this description illustrates exemplary, and with this description It is used to explain the principle of embodiment together.In figure,

Fig. 1 is the schematical sections perspective view of the exemplary of explosive motor；

Fig. 2 is the schematical sections perspective view of a part for the exemplary shown in Fig. 1；

Fig. 3 is the perspective illustration of the exemplary of the bent axle of the exemplary shown in Fig. 1；

Fig. 4 is the perspective illustration of the exemplary of the connecting rod of the exemplary shown in Fig. 1；

Fig. 5 A are the perspective illustrations of a part for the exemplary connecting rod shown in Fig. 4；

Fig. 5 B are the perspective illustrations of another part of the exemplary connecting rod shown in Fig. 4；

Fig. 6 is the diagrammatic top view of the exemplary shown in Fig. 1；

Fig. 7 is the schematic partial side sectional view obtained along the line A-A of Fig. 6；

Fig. 8 A are the schematical sections sectional views obtained along the line B-B of Fig. 7；

Fig. 8 B are the schematical sections sectional views obtained along the line C-C of Fig. 7；

Fig. 8 C are the schematical sections sectional views obtained along the line D-D of Fig. 7；

Fig. 9 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle shows It is 0 degree；

Fig. 9 B are that the signal of Fig. 9 A is schemed in detail；

Fig. 9 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle shows It is 0 degree；

Fig. 9 D are that the signal of Fig. 9 C is schemed in detail；

Fig. 9 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle shows It is 0 degree；

Fig. 9 F are that the signal of Fig. 9 E is schemed in detail；

Figure 10 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 15 degree；

Figure 10 B are that the signal of Figure 10 A is schemed in detail；

Figure 10 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 15 degree；

Figure 10 D are that the signal of Figure 10 C is schemed in detail；

Figure 10 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 15 degree；

Figure 10 F are that the signal of Figure 10 E is schemed in detail；

Figure 11 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 35 degree；

Figure 11 B are that the signal of Figure 11 A is schemed in detail；

Figure 11 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 35 degree；

Figure 11 D are that the signal of Figure 11 C is schemed in detail；

Figure 11 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 35 degree；

Figure 11 F are that the signal of Figure 11 E is schemed in detail；

Figure 12 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 90 degree；

Figure 12 B are that the signal of Figure 12 A is schemed in detail；

Figure 12 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 90 degree；

Figure 12 D are that the signal of Figure 12 C is schemed in detail；

Figure 12 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 90 degree；

Figure 12 F are that the signal of Figure 12 E is schemed in detail；

Figure 13 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 120 degree；

Figure 13 B are that the signal of Figure 13 A is schemed in detail；

Figure 13 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 120 degree；

Figure 13 D are that the signal of Figure 13 C is schemed in detail；

Figure 13 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 120 degree；

Figure 13 F are that the signal of Figure 13 E is schemed in detail；

Figure 14 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 150 degree；

Figure 14 B are that the signal of Figure 14 A is schemed in detail；

Figure 14 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 150 degree；

Figure 14 D are that the signal of Figure 14 C is schemed in detail；

Figure 14 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 150 degree；

Figure 14 F are that the signal of Figure 14 E is schemed in detail；

Figure 15 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown It is 180 degree to go out；

Figure 15 B are that the signal of Figure 15 A is schemed in detail；

Figure 15 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown It is 180 degree to go out；

Figure 15 D are that the signal of Figure 15 C is schemed in detail；

Figure 15 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown It is 180 degree to go out；

Figure 15 F are that the signal of Figure 15 E is schemed in detail；

Figure 16 A are the schematical sections end section figures obtained along the line B-B of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 270 degree；

Figure 16 B are that the signal of Figure 16 A is schemed in detail；

Figure 16 C are the schematical sections end section figures obtained along the line C-C of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 270 degree；

Figure 16 D are that the signal of Figure 16 C is schemed in detail；

Figure 16 E are the schematical sections end section figures obtained along the line D-D of Fig. 7, and the longitudinal axis angle of wherein bent axle is shown Go out is 270 degree；

Figure 16 F are that the signal of Figure 16 E is schemed in detail；

Figure 17 is similar to the schematic partial side sectional view of Fig. 7, and the another exemplary that it shows explosive motor is implemented A part for scheme；

Figure 18 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 0 degree；

Figure 18 B are that the signal of Figure 18 A is schemed in detail；

Figure 18 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 0 degree；

Figure 18 D are that the signal of Figure 18 C is schemed in detail；

Figure 18 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 0 degree；

Figure 18 F are that the signal of Figure 18 E is schemed in detail；

Figure 19 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 15 degree；

Figure 19 B are that the signal of Figure 19 A is schemed in detail；

Figure 19 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 15 degree；

Figure 19 D are that the signal of Figure 19 C is schemed in detail；

Figure 19 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 15 degree；

Figure 19 F are that the signal of Figure 19 E is schemed in detail；

Figure 20 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 35 degree；

Figure 20 B are that the signal of Figure 20 A is schemed in detail；

Figure 20 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 35 degree；

Figure 20 D are that the signal of Figure 20 C is schemed in detail；

Figure 20 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 35 degree；

Figure 20 F are that the signal of Figure 20 E is schemed in detail；

Figure 21 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 90 degree；

Figure 21 B are that the signal of Figure 21 A is schemed in detail；

Figure 21 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 90 degree；

Figure 21 D are that the signal of Figure 21 C is schemed in detail；

Figure 21 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 90 degree；

Figure 21 F are that the signal of Figure 21 E is schemed in detail；

Figure 22 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 120 degree；

Figure 22 B are that the signal of Figure 22 A is schemed in detail；

Figure 22 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 120 degree；

Figure 22 D are that the signal of Figure 22 C is schemed in detail；

Figure 22 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 120 degree；

Figure 22 F are that the signal of Figure 22 E is schemed in detail；

Figure 23 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 150 degree；

Figure 23 B are that the signal of Figure 23 A is schemed in detail；

Figure 23 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 150 degree；

Figure 23 D are that the signal of Figure 23 C is schemed in detail；

Figure 23 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 150 degree；

Figure 23 F are that the signal of Figure 23 E is schemed in detail；

Figure 24 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown It is 180 degree to go out；

Figure 24 B are that the signal of Figure 24 A is schemed in detail；

Figure 24 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown It is 180 degree to go out；

Figure 24 D are that the signal of Figure 24 C is schemed in detail；

Figure 24 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown It is 180 degree to go out；

Figure 24 F are that the signal of Figure 24 E is schemed in detail；

Figure 25 A are the schematical sections end section figures obtained along the line I-I of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 270 degree；

Figure 25 B are that the signal of Figure 25 A is schemed in detail；

Figure 25 C are the schematical sections end section figures obtained along the line H-H of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 270 degree；

Figure 25 D are that the signal of Figure 25 C is schemed in detail；

Figure 25 E are the schematical sections end section figures obtained along the line J-J of Figure 17, and the longitudinal axis angle of wherein bent axle is shown Go out is 270 degree；With

Figure 25 F are that the signal of Figure 25 E is schemed in detail.

Specific embodiment

Exemplary will be carried out now referring in detail to.In place of possible, the identical ginseng used in figure and description Examine numeral and refer to same or similar part.

Exemplary engine 10 shown in Fig. 1 to Figure 16 F is reciprocating piston, explosive motor.As shown in fig. 1, Engine 10 includes cylinder block 12.Exemplary cylinder body 12 defines many cylinders 14, and each cylinder defines longitudinal cylinder axis CL.Such as It is explained in more detail herein, some embodiments of exemplary cylinder body 12 can have than regular cyclical body phase to longer lengthL _B, to accommodate the bent axle with the crank-pin relatively longer than some conventional crank pins.

In the illustrated exemplary embodiment, engine 10 have inline configuration and four cylinders 14a, 14b, 14c and 14d.Although exemplary engine 10 has the construction of commonly referred to " four embed " construction, engine 10 can have ability Known other constructions of field technique personnel, such as（For example）Commonly referred to " V ", " W ", " H ", " flat ", " horizontally-opposed " and " footpath To " construction.In addition, although exemplary engine 10 has four cylinders, but engine 10 can have people in the art The cylinder of known other quantity of member, such as（For example）One, two, three, five, six, eight, 12,16, two Ten and 24.Therefore, engine 10 can for example have commonly referred to " four flat ", " six flat ", " in six It is embedding ", " V-6 ", " eight linear ", " V-8 ", " V-10 ", " V-12 ", the construction of " W-12 " and " H-16 " any one.This Outward, although exemplary engine described herein 10 is related to four operations of stroke, it is contemplated that those skilled in the art are Other operations known, such as（For example）Two strokes, three strokes, five strokes and six operations of stroke.Exemplary engine 10 can be spark ignition engine well known by persons skilled in the art, compression ignition engine, or its combination and/or change.

As shown in Figures 1 and 2, exemplary engine 10 includes the piston 16 corresponding to cylinder 14, such as four pistons 16a, 16b, 16c and 16d.As shown in fig. 1, piston 16a and 16d are respectively positioned at the upper end of cylinder 14a and 14d（I.e., relatively " top " of the orientation of the engine 10 shown in Fig. 1）, and piston 16b and 16c is due to being respectively positioned at cylinder 14b and 14c In lower section and it is invisible in Fig. 1.To a certain extent, the relative position of the piston 16 in cylinder 14 tends to indicating engine 10 relative ignition order（That is, the sequential order of the combustion case such as specified by cylinder）, exemplary engine 10 can be constructed To have difference ignition order as is known to persons skilled in the art.

The cylinder block 12 of exemplary engine 10 defines many bearings for receiving bent axle 20（It is not shown）So that bent axle 20 can rotate relative to cylinder block 12 along the North-south crankshaft axis CS defined by bent axle 20.For example, as shown in Figure 3, it is bent Axle 20 defines many crankshaft journals 22 with the circular cross section containing cross-section center.The quantity of crankshaft journal 22 correspond to by The number of bearings that cylinder block 12 is defined, and crankshaft journal 22 is by bearing receiving so that bent axle 20 can be along North-south crankshaft axis CS Rotation.

Although the quantity of crank-pin 24 is not necessarily equal to the quantity of piston 16, the exemplary song shown in Fig. 2 and Fig. 3 Axle 20 also defines the quantity of crank-pin 24 corresponding to the quantity of piston 16.As shown in Figure 3, each exemplary crank-pin 24 includes A pair of the crank-pin axle journals 25a and 25b, a pair two grades of crank-pins cam 27a and 27b separated by crank-pin cam 27, and a pair Three-level crank-pin cam 27c and 27d.In shown example, two grades of crank-pin cams 27a and 27b are located at crank-pin cam 27 Either side on, and three-level crank-pin cam 27c and 27d be located on the opposite sides of two grades of crank-pin cams 27a and 27b.According to Some embodiments（It is not shown）, bent axle 20 may include that two grades of crank-pin cam 27a of only one and only one three-level crank-pin are convex Wheel 27c.In such an implementation, two grades of crank-pin cam 27a can be located on the side of crank-pin cam 27, three-level crank-pin Cam 27c is located on two grades of sides relative with crank-pin cam 27 of crank-pin cam 27a so that crank-pin cam is by phase second wife It is set to crank-pin cam 27, two grades of crank-pin cam 27a and three-level crank-pin cam 27c.Or, two grades of crank-pin cam 27a The side of crank-pin cam 27 is can be located at, three-level crank-pin cam 27c is positioned at crank-pin cam 27 and two grades of crank-pin cams On 27a relative side so that crank-pin cam is three-level crank-pin cam 27c, crank-pin cam 27 and two grades by successive configurations Crank-pin cam 27a（As used herein, term " two grades " and " three-level " do not indicate relative importance.Conversely, these terms For by the structure of similar type from being distinguished from each other）.

Exemplary crank-pin axle journals 25a and 25b is circular cross section, and respective circular cross section can define center C（Example Such as see Fig. 8 A to Fig. 8 C）, it is then defined in the cross section for extending through respective crank-pin axle journals 25a and 25b in a vertical manner Longitudinal crank pin axis CP of heart C so that crank pin axis CP offsets parallel to crankshaft center line CS and relative to crankshaft center line CS. For example, longitudinal axis CS intervals of the crank pin axis CP away from bent axle 20 is a certain apart from T（See Fig. 3 and Fig. 9 A）.Bent axle 20 can also include Many counterpoises 26 are with offer（Or improve）The spin balancing of bent axle 20 when being assembled with piston 16 and connecting rod.In North-south crankshaft The line extended between axis CS and longitudinal crank pin axis CP defines the longitudinal axis RA of bent axle 20（See Fig. 9 A to Figure 16 F, and figure 18A to Figure 25 F）.

On exemplary crank-pin cam 27, such as shown in Fig. 8 A, crank-pin cam 27 is defined and corresponded to from crank-pin Radial distances of the axis CP to the edge surface 31 of crank-pin cam 27r _dCam contour 29.Radial distancer _dFrom smallest radial Distance change is to maximum radial distance defining cam contour 29.Exemplary according to Fig. 8 A, crank-pin The cam contour 29 of cam 27 defines general crowning radius, wherein a part for cam contour 29 for cam contour 29 extremely It is few about 70 degree（For example, at least about 80 degree, at least about 90 degree, at least about 100 degree, at least about 110 degree, at least about 120 degree, At least about 130 degree, at least about 140 degree or at least about 150 degree）With less constant radius.It is convex according to some embodiments Wheel profile 29 can have at least about 70 degree defined for cam contour（For example, at least about 80 degree, at least about 90 degree, at least about 100 degree, at least about 110 degree, at least about 120 degree, at least about 130 degree, at least about 140 degree or at least about 150 degree）It is less constant Radial distancer _dPart.

In fig. 8 a in shown exemplary, along from North-south crankshaft axis CS towards longitudinal crank pin axis The first direction that the line of CP extendsd ₁On, with first directiond ₁Relatively radial distancer _d1Less than maximum radial distance.In addition, Along from longitudinal crank pin axisC PTowards North-south crankshaft axisC SLine extend second directiond ₂On, with second directiond ₂Relatively radial distancer _d2More than with first directiond ₁Relatively radial distancer _d1。

Similar in appearance to crank-pin cam 27, the second crank-pin cam 27a and 27b is defined and corresponded to from crank pin axisC PPoint It is clipped to two grades of radial distances of the edge surface 31a and 31b of crank-pin cam 27a and 27br _d ’Two grades of cam contour 29a and 29b, as seen in fig. 8b.Radial distancer _d ’Maximum radial distance is changed to from minimum radial distance to define two grades of cam wheels Wide 29a and 29b.As seen in fig. 8b, along from North-south crankshaft axisC STowards longitudinal crank pin axisC PLine extend First directiond ₁On, with first directiond ₁It is relatively radial apart from r_d ’ ₁Less than maximum radial distance.In addition, along from Longitudinal crank pin axisC PTowards the second direction that the line of North-south crankshaft axis CS extendsd ₂On, with second directiond ₂Related Radial distancer _d ’ ₂More than with first directiond ₁Relatively radial distancer _d ’ ₁.According to some embodiments, two grades of cam contours 29a and 29b can be generally with crank-pin cam 27 cam contour 29 it is identical.According to some embodiments, two grades of cam contours 29a and 29b can be generally from crank-pin cam 27 cam contour 29 it is different.

Three-level crank-pin cam 27c and 27d are defined and corresponded to from crank pin axisC PThree-level crank-pin cam is arrived respectively The radial distance of the edge surface 31c and 31d of 27c and 27dr _d ’’Three-level cam contour 29c and 29d, as seen in fig. 8 c.Footpath To distancer _d ’’Maximum radial distance is changed to from minimum radial distance to define three-level cam contour 29c and 29d.As in Fig. 8 C It is shown, along from North-south crankshaft axisC STowards longitudinal crank pin axisC PLine extend first directiond ₁On, with One directiond ₁Relatively radial distancer _d ’’ ₁Less than maximum radial distance.In addition, along from longitudinal crank pin axis CP towards vertical To the second direction that the line of crankshaft center line CS extendsd ₂On, with second directiond ₂Relatively radial distancer _d ’’ ₂More than with first Directiond ₁Relatively radial distancer _d ’’ ₁。

According to some embodiments, 29, two grades of cam contour 29a and 29b and three-level cam contour 29c of cam contour and 29d can be different each other.According to some embodiments, cam contour 29, two grades of cam contours 29a and 29d, and three-level cam wheel One or more in wide 29c and 29d can be substantially the same.For example, cam contour 29, two grades of cam contours 29a and 29d, and One or more in three-level cam contour 29c and 29d can be substantially the same, but on crank pin axisC PRelative to that This rotation.

With reference to Fig. 2, piston 16 is operatively coupled to via a quantity of respective connecting rod 28 corresponding to the quantity of piston 16 Crank-pin 24.For example, exemplary connecting rod 28（For example see Fig. 4）Including the near-end 30 with elliptical openings 32a and 32b, and tool There is the distal end 34 in the second aperture 36.The near-end 30 of exemplary connecting rod 28 is operatively coupled to song via elliptical openings 32a and 32b The crank-pin 24 of axle 20, and the distal end 34 of connecting rod 28 is operatively coupled to piston 16 via pin 38.

As shown in Fig. 4, Fig. 5 A and Fig. 5 B, exemplary connecting rod 28 includes bar portion 33 and cap 35.The He of exemplary bar portion 33 Exemplary cap 35 defines elliptical openings 32a and 32b, and each defines the longitudinal axis to wherein elliptical openings 32a and 32b, and it can one As parallel to connecting rod 28 the longitudinal axisC RAnd extend.Elliptical openings 32a and 32b define the width orthogonal with the longitudinal axis, the width Degree corresponds generally to the cross-sectional diameter of crank-pin axle journals 25a and 25b, so as to allow crank-pin axle journals 25a and 25b relative to even Bar 28 is linearly mobile.This representative configuration allows longitudinal crank pin axisC PRelative line and the near-end 30 of connecting rod 28 between Property motion.

As shown in Fig. 4 and Fig. 5 A, exemplary bar portion 33 include first couple of supporting leg 37a and 37b, and with first pair of supporting leg Second couple of supporting leg 39a and 39b 37a and 37b spaced apart, so as to provide space between first pair of supporting leg and second pair of supporting leg 41.First couple of supporting leg 37a and 37b at least partly define the first elliptical openings 32a, and second couple of supporting leg 39a and 39b at least portion The fixed second elliptical openings 32b of boundary.

In fig. 4 in shown exemplary, sleeve 46 may be provided in elliptical openings 32a and 32b.Example Such as, the exemplary sleeve 46 shown in Fig. 4 includes half sleeve 48, and it defines the axle journal 25a and 25b for receiving crank-pin 24 In the bearing surface 50 of.Half sleeve 48 includes opposed flange 52 so that when in elliptical openings 32a and 32b During assembling sleeve 46, supporting leg is sandwiched between the opposed flange 52 of respective sleeve 46 to 37a and 37b and 39a and 39b.Sleeve 46 permission crank-pins 24 are moved back and forth in elliptical openings 32a and 32b, while providing bearing surface 50, crank-pin axle journals 25a Rotated in the bearing surface with 25b.

As shown in figs. 5 a and 5b, bar portion 33 include the follower 43 and second follower 43a related to space 41 and 43b.For example, in the illustrated exemplary embodiment, follower 43 and second follower 43a and 43b are located at first pair of supporting leg In 37a and 37b and second pair of space 41 of the apex of supporting leg 39a and 39b.The bar portion 33 of connecting rod 28 is couple to bent axle 20 and causes First couple of supporting leg 37a and 37b and second couple of supporting leg 39a and 39b respectively with the first crank-pin axle journals 25a and the second crank pin Neck 25b is related, wherein the cam 27 of crank-pin 24, and two grades of cams 27a and 27b, and three-level cam 27c and 27d are positioned at sky In gap 41（See Fig. 2）.Exemplary cap 35（See Fig. 5 B）Can be by bonnet bolt（It is not shown）Be couple to first couple of supporting leg 37a and 37b and second couple of supporting leg 39a and 39b, so as to seal respective elliptical openings around respective crank-pin axle journals 25a and 25b 32a and 32b, its cam 27, two grades of cams 27a and 27b, and three-level cam 27c and 27d are restricted to the space 41 of connecting rod 28 In.Some embodiments may include to correspond to two grades of follower 43a of only one of two grades of crank-pin cam 27a, and/or right The Ying Yuyi only one three-level follower 42c of three-level crank-pin cam 27c.

Exemplary according to Fig. 5 A, exemplary follower 43 and two grades of followers 43a and 43b are by structure Make to be swung relative to bar portion 33 to reduce between respective crank-pin cam 27 and follower 43 and respective two grades of crank-pins are convex Friction and wear of the wheel between 27a and 27b and two grade of follower 43a and 43b.Follower 43 and two grades of followers 43a and 43b can Formed by individual construction so that it swings together each other.According to some embodiments, follower 43 and two grades of follower 43a and 43b can be formed independently from each other so that it swings independently from each other.According to some embodiments, two grades of followers 43a and 43b Can be configured to be swung together but independently of follower 43.

Follower 43 may include follower surface, its concave for being shaped to provide adjacent cams 27 surfaces, its with When power stroke starts（For example, in longitudinal axisR AAngle Position terminate consistent with the delay that power stroke starts, for example, Work as longitudinal axisR AMore than the first stroke ends angleθ ₁At 35 degree（For example see Figure 11 A））The complementary convex surface of cam contour 29 half Footpath is substantially the same.For example, follower 43 can have follower surface, it has with the crowning radius of cam contour 29 Divide substantially the same concave, at least about 70 degree of a part for cam contour 29 of the crowning radius（For example, right In at least about 80 degree, at least about 90 degree, at least about 100 degree, at least about 110 degree, at least about 120 degree, at least about 130 degree, at least About 140 degree, or at least about 150 degree）With substantially the same radius.This representative configuration can be used for increase cam 27 with Contact area between moving part 43, so as to reduce the friction and/or abrasion of cam 27 and/or follower 43.

According to some embodiments（For example, the exemplary shown in Figure 17 to 25F）, two grades of follower 43a Respective follower surface is may include with 43b, the concave surface that it is shaped to the surface with two neighboring stages cam 27a and 27b half Footpath, it is substantially the same with the complementary convex surface radius of two grades of cam contours 29a and 29b for example when power stroke starts.For example, Two grades of followers 43a and 43b can have follower surface, and it has and two grades of crowning radius of cam contour 29a and 29b of cam A part of substantially the same concave, the crowning radius are for two grades at least about 70 degree of cam contour 29a and 29b （For example, at least about 80 degree, at least about 90 degree, at least about 100 degree, at least about at least about 110 degree, 120 degree, at least about 130 Degree, at least about 140 degree, or at least about 150 degree）With substantially the same radius.This representative configuration can be used for increase by two Level crank-pin cam 27a and 27b and the contact area between respective two grades of followers 43a and 43b, so as to reduce by two grades of cams 27a and 27b and/or two grade of friction and/or abrasion of follower 43a and 43b.

In figure 9 a in shown exemplary, the also complementary table including adjacent rod portions 33 of exemplary follower 43 The crowning radius in face, follower 43 swings against the complementary surface.This representative configuration can be used to increase follower 43 And the contact area between the surface of bar portion 33, so as to reduce the friction and/or abrasion of bar portion 33 and/or follower 43.It is similar Ground, as shown in Figure 9 C, the crowning radius of exemplary two-stage follower 43a and the 43b also complementary surface including adjacent rod portions 33, Two grades of followers 43a and 43b swing against it.This representative configuration can be used to increase by two grades of follower 43a and 43b and bar Contact area between the surface in portion 33, so as to reduce friction and/or the mill of bar portion 33 and/or bar two grades of followers 43a and 43b Damage.

According to some embodiments, follower 43 and/or two grades of followers 43a and 43b may include deep-slotted chip breaker（It is not shown）, And bar portion 33 may include pin（It is not shown）So that as the surface of cam 27 and two grades of cams 27a and 27b bears against follower 43 and two grades of followers 43a and 43b ride, follower 43 and two grades of follower 43a and 43b swing relative to bar portion 33.This can For increased contact surface between the apparent surface and bar portion 33 for maintaining follower 43,43a and 43b and cam 27,27a and 27b Product, so as to reduce the friction and/or abrasion of cam 27,27a and 27b, bar portion 33 and/or follower 43,43a and 43b.

Can be used lubricant that the friction and/or abrasion of the relative motion between respective cam and follower are come to reduce. For example, it is possible to provide lubricant with reduce follower 43,43a and 43b one or more surfaces and cam 27,27a and 27b it is each From friction and/or abrasion between surface.According to some embodiments, one or more surfaces of follower 43,43a and 43b Hydrodynamic lubrication or fluid film profit between being configured to promote respective surface with the respective surface of cam 27,27a and 27b It is sliding.

In figure 5b in shown exemplary, the cap 35 of connecting rod 24 includes respective three-level follower 43c And 43d, it is configured to follow respective three-level crank-pin cam 27c and 27d.For example, the example shown in Fig. 4 and Fig. 5 B Property embodiment in, three-level follower 43c and 43d be located at elliptical openings 32a and 32b lid end apex.Connecting rod 28 Bar portion 33 and cap 35 be couple to bent axle 20 so that three-level crank-pin cam 27c and 27d respectively with three-level follower 43c and 43d Alignment.Some embodiments may include an only one three-level crank-pin cam 27c and three-level follower 43c.Three-level crank-pin Cam 27c and 27d and three-level follower 43c and 43d can be used for during the induction stroke of engine 10（That is, when engine 10 When being four-stroke engine）Connecting rod 28 and piston 16 are pulled downward on along cylinder 14, is acted on piston 16 in shortage in the meantime Combustion force in the case of the operation of bent axle 20 along cylinder 14 pull downward on piston 16.Three-level crank-pin cam 27c and 27d and three Interaction between level follower 43c and 43d by the pulling force from crank-pin 24 via three-level crank-pin cam 27c and 27d, Three-level follower 43c and 43d and connecting rod 28 by prevent crank-pin 24 in unrestricted mode in elliptical openings 32a and Slided in 32b and be transferred to piston 16.

As shown in Figure 5 B, connecting rod 28 may include a cap 35, and it is for example via such as bolt（It is not shown）Fastener And it is couple to first pair of supporting leg and second couple of supporting leg 37a, 37b, 39a and 39b.As shown（For example see Figure 10 A）, exemplary cap 35 include thering is chamber 66（For example, hole）Lid recess 64.In the illustrated exemplary embodiment, lid recess 64 includes thering is arc The one end 68 in shape face, and lid recess 64 receives rocker member 70, it has containing the end 68 relative to lid recess 64 with complementation side The one end on the curved surface 72 of formula, to facilitate the motion between rocker member 70 and cap 35, such as oscillating motion.In chamber 66 Biasing member 74 can be provided to bias rocker member 70 so that its lid recess 64 relative to cap 35 and pivot out（For example see Fig. 9 E and Fig. 9 F）.Biasing member 74 may include any of bias configuration, such as（For example）One or more springs, hydraulic pressure are total Into and/or air pressure assembly.

According to some embodiments, rocker member 70 may include to receive the groove 54 of three-level follower 43c and 43d（For example, With arc-shaped cross-section）, three-level the follower 43c and 43d have the respective surface with the complementation of groove 54 so that three-level is servo-actuated Part 43c and 43d can swing or usually move in addition in groove 54.Three-level follower 43c and 43d are installed on follower base portion 44 opposite end（For example see Fig. 5 B）, and therefore three-level follower 43c and 43d swung also relative to cap 35 or in addition usually It is mobile.According to some embodiments, rocker member 70 may include one of adjacent grooves 54 and three-level follower 43c and 43d or Multiple projections 45, it helps prevent three-level follower 43c and 43d in embedded groove 54 during swinging.

Exemplary rocker member 70 can be used to generally maintain respective three-level crank-pin cam 27c and 27d to be servo-actuated with three-level Contact between part 43c and 43d.For example, as shown in Figure 11 E, Figure 11 F, Figure 12 E and Figure 12 F, rocker member 70 is relative to lid Portion 35 pivots, and wherein biasing member 74 provides bias force and is held against respective three-level crank with by three-level follower 43c and 43d Pin cam 27c and 27d.Friction, abrasion and/or noise are reduced during this operation that can cause engine 10.

According to shown exemplary, three-level follower 43c and 43d may include follower surface, and it is concave surface So that it provides the more large access area with the cam contour 29c and 29d of three-level crank-pin cam 27c and 27c.For example, servo-actuated Part surface can have concave, its minimum crowning radius for corresponding to three-level crank-pin cam 27c and 27d.According to some realities Apply scheme（For example, as shown）, the follower surface of three-level follower 43c and 43d can be constructed such that it across respective three-level At least one of at least two discrete contact points of the width of crank-pin cam 27c and 27d and three-level follower 43c and 43d Place contacts three-level crank-pin cam 27c and 27d（For example see Fig. 9 F, Figure 10 F, Figure 11 F, Figure 12 F, Figure 13 F, Figure 14 F, Figure 15 F and Figure 16 F）.This can be used to reducing three-level crank-pin cam 27c and 27d and the friction between three-level follower 43c and 43d and/or Abrasion.

According to some embodiments, with the surface of three-level crank-pin cam 27c and 27d against three-level follower 43c and 43d rides and by three-level follower 43c and 43d, and follower 43c and 43d swings relative to cap 35, such as Fig. 9 F, figure Shown in 10F, Figure 11 F, Figure 12 F, Figure 13 F, Figure 14 F, Figure 15 F and Figure 16 F.This can be used to maintain three-level follower 43c and 43d The increased contact area and the surface of three-level crank-pin cam 27c and 27d between, thus reduce three-level crank-pin cam 27c and The friction and/or abrasion of 27d and/or three-level follower 43c and 43d.

Can be used lubricant come from reducing the relative motion between respective three-level cam and three-level follower friction and/ Or abrasion.For example, it is possible to provide lubricant is reducing one or more surfaces of three-level follower 43c and 43d and three-level cam 27c And friction and/or abrasion between the respective surface of 27d.According to some embodiments, one of three-level follower 43c and 43d Or the respective surface of multiple surfaces and three-level cam 27c and 27d can be configured to promote the hydrodynamic between respective surface to moisten Sliding or fluid film lubrication.

Crank-pin cam 27, two grades of crank-pin cams 27a and 27b, three-level cam 27c and 27d, 43, two grades of follower with One or more in moving part 43a and 43b and three-level follower 43c and 43d can be by being configured to undergo and cam and follower Between the hardened material of the related friction of interaction formed.For example, one or more of cam and follower can be by abilities The known hardening bearing material of field technique personnel is formed.According to some embodiments, 43, two grades of follower 43a of follower and One or more modes that can be biased in 43b, three-level follower 43c and 43d are installed so that follower is biased to contact Correspondence cam.This bias force can be provided for example by spring, hydraulic bias power and/or air pressure bias force.This biasing can For example for maintain crank-pin cam 27, two grades of crank-pin cam 27a and 27b and three-level crank-pin cam 27c and 27d with it is respective 43, two grades of follower 43a and 43b of follower and the contact between three-level follower 43c and 43d, and/or reduce and operation example The noise of the property correlation of engine 10.

According to some embodiments, crank-pin cam 27, two grades of crank-pin cam 27a and 27b, three-level crank-pin cams One or more in 27c and 27d, 43, two grades of follower 43a and 43b of follower and three-level follower 43c and 43d can be by structure Make so that one or more cams run through longitudinal axisR A360 degree rotation keep connect with corresponding one or more followers Touch.In this exemplary manner, the relative motion between crank-pin 24 and connecting rod 28 can run through longitudinal axisR A360 degree rotation Then more closely control.According to some embodiments, the relative motion between crank-pin 24 and connecting rod 28 possibly cannot run through Longitudinal axisR AIt is whole 360 degree rotation and nearly control.

During the operation of conventional engine, piston is moved back and forth in cylinder so that rushed in the power of explosive motor During journey, the burning of the air/fuel mixture in the combustion chamber defined by piston, cylinder and cylinder head is forced the piston towards To bent axle.As piston is advanced towards bent axle, bent axle rotates via connecting rod and crank-pin, so as to the air/fuel with compression be mixed The related potential energy of compound is converted to mechanical work.

Yet with the framework of conventional internal combustion engine, when piston is in meets the position of maximum compression in cylinder（That is, Combustion chamber is in its minimum capacity, and this condition conforms generally to maximum compression when piston is farthest away from bent axle）, in bent axle Radially extending axis tends to almost conllinear with pitman shaft between the heart and the center of crank-pin（If without conllinear）.In these phases To position, it is first begin to towards the motion of bent axle during power stroke with piston, only with pitman shaft and longitudinal axis Between extend the very short arm of force（If any）.As a result, the power for initially being created in burning by air/fuel mixture cannot If torque big as the torque with the length of the arm of force when bigger by conversion is delivered into bent axle.Such case may especially not Expect because during burning and burning after soon, the power on piston may be close to its maximum magnitude due to combustion case. Additionally, with piston be travel downwardly towards bent axle along cylinder and the arm of force length increase, act on piston from combustion case On the value of power can dissipate rapidly.Consequently, because in pitman shaft and longitudinal axis during the time of maximum, force on piston Between create the very short arm of force, so in conventional internal combustion engine from combustion process produce work(efficiency be likely less than expectation Efficiency.

By contrast, during the operation of exemplary engine 10, as bent axle 20 rotates, crank-pin 24 is around the bent axle longitudinal axisC SRotation so that crank pin centerCCircular path is defined, it has by along the longitudinal axis in bent axle 20C SWith respective song The longitudinal axis of handle pin 24C PBetween radially extending axisR A（For example see Fig. 3 and Fig. 9 A）The distance for definingTAnd half for defining Footpath.Therefore, the near-end 30 of connecting rod 28（Its elliptical openings 32a and 32b via connecting rod 28 and be couple to crank-pin 24）It is based on The profile of crank-pin cam 27,27a, 27b, 27c and 27d and move, such as solve in more detail on Fig. 9 A to Figure 25 F below Release.The distal end 34 of connecting rod 28 is limited to be moved in reciprocal and linear mode due to being operatively coupled to piston 16, described Piston 16 is similarly limited to be moved in the respective cylinder 14 defined by cylinder block 12 in reciprocal and linear mode.As a result, with Bent axle 20 to rotate, piston 16 is moved back and forth in respective cylinder 14, is defined and is corresponded generally to crank pin axisC PWith bent axle AxisC SThe distance betweenTTwice piston stroke（It is such as impacted according to exemplary operation described herein）.

As for exemplary engine 10, follower 43 is ridden against crank-pin cam 27, two grades of followers 43a and 43b are supported Ridden by two grades of crank-pin cams 27a and 27b, and three-level follower 43c and 43d is against three-level crank-pin cam 27c and 27d Ride.Radial distance with cam contour changes, the near-end 30 of connecting rod 28 by means of along the longitudinal axis in elliptical openings 32a and Reciprocating crank-pin axle journals 25a and 25b in 32b（See Fig. 3）And relative to longitudinal crank pin axisC PIt is linear mobile, such as It is explained in more detail on Fig. 9 A to Figure 25 F.Due to this representative configuration, the stroke of example piston 16 is according to crank-pin cam 27th, 27a, 27b, 27c and 27d and respective follower 43, the interaction between 43a, 43b, 43c and 43d and it is impacted.Such as It is explained in more detail herein, this representative configuration can allow to customize the operating characteristic of exemplary engine 10（For example, power is defeated Go out, torque, efficiency and/or response）.

Exemplary according to Fig. 9 A to Figure 25 F, it is this mutual between crank-pin 24 and connecting rod 28 Effect can be constructed such that during power stroke piston 16 is merely deferred until that bent axle 20 has rotated towards the substantial motion of bent axle 20 To in the combustion force being transferred on piston 16 and in crankshaft center lineC SWith respective crank pin axisC PBetween it is radially extending AxisR ABetween have the more effective arm of force when untill.For example, crank-pin cam can be formed so that in the distal end of connecting rod 28 34 open as bent axle 20 rotates without any motion or without crank-pin 24 in the case of any notable amount of exercise in ellipse Moved in mouth 32a and 32b, so as to be effectively increased the center of crank-pin 24CThe distance between with the distal end 34 of connecting rod 28.As a result, A greater amount of energy of combustion case can be captured, because the maximum power acted on piston 16 meets the bigger arm of force, so that Cause torque bigger at bent axle 20 during power stroke.The time that burning starts can be customized and postpone stroke with utilization.

If for example, in the longitudinal axis of bent axle 20R AIn 0 degree when piston 16 will generally reverse its direct of travel, that Piston 16 can（1）Its stroke endpoint is reached as longitudinal axis RA is in zero degree, and it is straight then to postpone the reverse in its direction To it there is the bigger arm of force between connecting rod 28 and crankshaft center line CS, or（2）Even 0 degree follow-up has been reached in longitudinal axis RA Continue and moved up in the side for leaving bent axle 20 in cylinder 14, and postpone the reverse in its direction until connecting rod 28 and crankshaft center line CS Between exist the bigger arm of force untill.As a result, a greater amount of energy of combustion case can be captured, because acting on piston 16 most Big power meets the bigger arm of force, so as to cause power stroke during torque bigger at bent axle 20.

Fig. 9 A to Figure 16 F schematically illustrate the exemplary operation of the engine 10 with representative configuration, and it can be used to prolong Slow piston 16 engine 10 stroke initially along the downward traveling of cylinder 14.For example, the follower 43,43a of connecting rod 28, The cam 27,27a, 27b, 27c and 27d of 43b, 43c and 43d and crank-pin 24 interacts, cause crank-pin axle journals 25a and 25b（See Fig. 3）Moved back and forth in elliptical openings 32a and 32b, so as to effectively change the effective length of connecting rod 28.Such as Fig. 8 A Shown in, cam contour 29,29a and 29b are away from longitudinal crank pin axisC PRespective radial distancer _d 、r _d ’Withr _d ’’Change Become so that crank-pin 24 can without move connecting rod 28 distal end 34 in the case of in elliptical openings 32a and 32b with Bent axle 20 rotates and moves, so as to be effectively increased the center of crank-pin 24CThe distance between with the distal end 34 of connecting rod 28.It is this Representative configuration causes or even is continued around as bent axle 20 rotates in crank-pin 24 axis of bent axle 20C SStill may be used during rotation Piston 16 is maintained at the generally fixed position in cylinder 14 in shorter time period.According to some embodiments, piston 16 can continue to be travelled upwardly along cylinder 14 in shorter time period.As a result, piston 16 can be maintained the highest in combustion chamber At pressure spot, while crank-pin 24 is rotated to causing by transmitting effect in the power on piston 16 and in the center of bent axle 20 and crank The center of pin 24CBetween radially extending axisR AAt the increased position of the arm of force defined.This causes relatively more torques Bent axle 20 is applied to as burning starts, wherein piston 16 is at the farthest point in the center away from bent axle 20（That is, as institute Show, in the end of its up stroke）.In this exemplary manner, the delay policy of following summary can be implemented.

The limited energy of various example arrangements is illustrated for the purpose for clearly describing and due to the section of Fig. 9 A to Figure 16 F Power, although the exemplary on Fig. 9 A to Figure 16 F descriptions includes crank-pin axle journals to 25a and 25b（See Fig. 3）, it is ellipse , to 32a and 32b, to 27a and 27b, two grades of followers are to 43a and 43b, and three-level crank-pin is convex for two grades of crank-pin cams for circular open Wheel is to 27c and 27d, and three-level follower is to 43c and 43d, but following description will refer to crank-pin axle journals, elliptical openings, Two grades of crank-pin cams, two grades of followers, three-level crank-pin cam and three-level followers it is respective to only one.Such as institute above State, some alternate embodiments may include crank-pin axle journals, elliptical openings, two grades of crank-pin cams, two grades of followers, three-levels Only one in crank-pin cam and/or three-level follower（That is, it is opposite with paired）.

As shown in Fig. 9 A to Fig. 9 F, bent axle 20 is oriented such that the center at the center and crank-pin 24 by bent axle 20CBoundary Fixed longitudinal axisR AZero degree is oriented, its compression stroke for corresponding generally to conform generally to exemplary engine 10（With Exhaust stroke in four-stroke engine）The the first stroke ends angle terminatedθ ₁.Therefore, with longitudinal axisR AIt is fixed with this To piston 16 is located orientation thereon in cylinder 14 and put.According to some embodiments, piston 16 can be in this longitudinal axis position Continuation is travelled upwardly along cylinder 14.

As shown in figs. 9 a and 9b, during the operation of engine 10, bent axle 20 rotates in the clockwise direction.With Crank-pin cam 27 and follower 43 interact as shown, crank-pin axle journals 25a（See Fig. 3）It is normally at elliptical openings Center in the length of 32a so that piston 16 in its top of stroke, while the longitudinal axis of bent axle 20R AIt is vertical with connecting rod 28 AxleC RIn general alignment with.This position and representative configuration cause the center of crank-pin 24CWith the distal end 34 of connecting rod 28（Example Such as, the center in the second aperture 36）The distance between relative to the crank-pin 24 for example shown in Figure 11 A to Figure 15 F centerC It is reduced with the distance between the distal end 34 of connecting rod 28.

As shown in figs. 9 a and 9b, exemplary crank-pin cam 27 and follower 43 do not contact with each other.Particularly, it is convex Take turns the radial distance of profile 29r _dIt is short enough so that crank-pin cam 27 does not contact follower 43.But Fig. 9 C and Fig. 9 D are referred to, Two grades of crank-pin cam 27a and two grades of follower 43a contact with each other, and thus be accordingly used in the center of control crank-pin 24CWith connecting rod The distance between 28 distal end 34 and/or or crank-pin axle journals 25a along the longitudinal axis of elliptical openings 32a lengthwise position.

With reference to Fig. 9 E and Fig. 9 F, three-level cam 27c and three-level follower 43c contact with each other, and therefore can control closely ellipse The lengthwise position of the crank-pin axle journals 25a in circular open 32a.Biasing member 74 provides the bias force against rocker member 70, So as to three-level follower 43c be kept to be contacted with three-level cam 43c.

Referring to figures 10A to Figure 10 F, bent axle 20 is in longitudinal axisR ARotate more than the first stroke ends angleθ ₁ 15 The orientation of degree.In conventional engine, piston 16 will be with longitudinal axisR ARotation is had begun to towards bent axle by 15 degree AxisC SAdvance.By contrast, according to exemplary engine 10, piston 16 not yet starts it towards crankshaft center lineC SDownward Advance.According to some embodiments, piston 16 can actually more than the first stroke ends angleθ ₁When between 0 degree and 15 degree after It is continuous to be advanced slightly upward along cylinder 14.As shown in Figure 10 A and 10 B, crank-pin cam 27 just starts to contact follower 43, The surface radius of wherein follower 43 are slightly lower than the surface radius of crank-pin cam 27.

With reference to Figure 10 C and Figure 10 D, two grades of crank-pin cam 27a and two grades of follower 43a keep contact, wherein two grades convex The radial distance of wheel profile 29ar _d ’Increase so that crank-pin axle journals 25a（See Fig. 3）Along elliptical openings 32a longitudinal directions to moving down It is dynamic, so as to increase the effective length of connecting rod 28（That is, the center of crank-pin 24 is increasedCAnd the distal end 34 of connecting rod 28 between away from From）.As a result, piston 16 not starts to be travel downwardly along cylinder 14, and opposite piston 16 is maintained at the end of its up stroke（Or after It is continuous to be travelled upwardly along cylinder 14）.As shown in fig. 10d, exemplary two-stage crank-pin cam 27a and exemplary two-stage follower 43a is constructed such that the longitudinal axis in bent axle 20R AThis position at two grades of surface radius of crank-pin cam 27a with The radius of two grades of adjacently situated surfaces of follower 43a is similar.

With reference to Figure 10 E and Figure 10 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and therefore The lengthwise position of the crank-pin axle journals 25a in elliptical openings 32a continues to be controlled closely.Biasing member 74 continue provide against The bias force of rocker member 70, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.

In Figure 11 A to Figure 11 F, bent axle 20 has rotated into longitudinal axisR AMore than the first stroke ends angleθ ₁35 degree Orientation.In conventional engine, piston 16 will be with longitudinal axisR ARotation is by 35 degree towards crankshaft center lineC S Advance a certain obvious distance.By contrast, according to exemplary engine 10, piston 16 not yet starts it towards crankshaft center lineC STo Under traveling.Replace, two grades of crank-pin cam 27a rotate relative to two grades of follower 43a（See Fig. 9 C, Figure 10 C and figure 11C）So that the interaction between two grades of crank-pin cam 27a and two grades of follower 43a causes crank-pin axle journals 25a（See figure 3）In elliptical openings 32a（With shown orientation）It is downward in the way of causing the distal end 34 of connecting rod 28 generally without motion Move to the position of the core further from elliptical openings 32a.Particularly, two grades of radial distances of cam contour 29ar _d ’Increase（Compared with Fig. 9 C and Figure 11 C）, so as to force crank-pin axle journals 25a downward along elliptical openings 32a.As a result, it is bent The center of handle pin 24CWith the distance between the distal end 34 of connecting rod 28 relative to the crank-pin 24 shown in Fig. 9 A and Fig. 9 B CenterCIncrease with the distance between the distal end 34 of connecting rod 28.Due to apart from upper this increase, even if the phase of crank-pin 24 For the center of bent axle 20CTurn clockwise so that the center of crank-pin 24C PTop away from cylinder 14 is farther, piston 16 It is travel downwardly along cylinder 14 again without beginning.According to some embodiments, piston 16 can actually more than the first stroke end Angle tillθ ₁Continue to be advanced slightly upward along cylinder 14 when between 0 degree and 35 degree.

As shown in Figure 11 A and Figure 11 B, crank-pin cam 27 is contacted with follower 43 now, wherein the table of follower 43 Radius surface is about identical with the surface radius of crank-pin cam 27（For example, identical）.By means of crank-pin cam 27 and follower 43 Respective surface radius it is similar or identical, the contact area between two surfaces is bigger, and it can be used for the power in engine 10 During stroke（And when engine 10 is four-stroke engine, during induction stroke）Reduce crank-pin cam 27 and follower Friction and/or abrasion between 43 surface.

In shown example, the radial distance of crank-pin cam 27 at the point or surface contacted with follower 43r _dIncrease Plus, so as to increase the effective length of connecting rod 28.As a result, piston 16 is travel downwardly not along cylinder 14, and opposite piston 16 is maintained at The end of its up stroke, or in some embodiments, continuation is travelled upwardly along cylinder 14.Compared to Figure 10 D, such as scheme Shown in 11D, exemplary two-stage cam 27a and two grades of follower 43a no longer contact with each other, and therefore crank-pin cam 27 with Crank-pin axle journals 25a in contact control elliptical openings 32a between moving part 43（See Fig. 3）Lengthwise position.

As shown in Figure 11 E and Figure 11 F, three-level cam 27c and three-level follower 43c keeps contacting with each other, and therefore leads to Cross crank-pin cam 27, follower 43, three-level cam 27c and three-level follower 43c and control elliptical openings 32a closely The lengthwise position of crank-pin axle journals 25a.Biasing member 74 continue provide against rocker member 70 bias force, so as to by three-level with Moving part 43c keeps being contacted with three-level cam 43c.

As shown in Figure 12 A to Figure 12 F, bent axle 20 has rotated into longitudinal axisR AMore than the first stroke ends angleθ ₁90 The orientation of degree.Compared to Fig. 9 A to Figure 11 F, piston 16 has started to it towards crankshaft center line nowC SDownward traveling.Such as Figure 12 A Shown in Figure 12 B, crank-pin cam 27 keeps being contacted with follower 43, and the surface radius of follower 43 continue and crank-pin The surface radius of cam 27 are similar（For example, identical）.As shown in figure 12a, it is bent at the point or surface contacted with follower 43 The radial distance of handle pin cam 27r _dIts maximum is approximately in, causes crank-pin axle journals 25a（See Fig. 3）It is approximately in along ellipse Circular open 32a downward maximum lengthwise position so that the effective length of connecting rod 28 is approximately in its maximum.As in Figure 12 D It is shown, exemplary two-stage crank-pin cam 27a and two grades of follower 43a continue not with contact with each other.As a result, crank-pin cam 27 The lengthwise position of crank-pin axle journals 25a in the control elliptical openings of the contact between follower 43 32a.

As shown in Figure 12 E and Figure 12 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore by crank-pin cam 27, follower 43, three-level crank-pin cam 27c and three-level follower 43c and control ellipse closely The lengthwise position of the crank-pin axle journals 25a in the 32a of shape opening.Biasing member 74 continues to provide the biasing against rocker member 70 Power, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.However, as shown in Figure 12 E and Figure 12 F, Lid recess 64 of the rocker member 70 no longer substantially with the cap 35 of connecting rod 28 is spaced apart, wherein three-level crank-pin cam 27c and three Interaction compression biasing member 74 between level follower 43c.

With reference to Figure 13 A to Figure 13 F, bent axle 20 has rotated into longitudinal axisR AMore than the first stroke ends angleθ ₁120 degree Orientation.Piston 16 continues to be travel downwardly along cylinder 14.Crank-pin cam 27 keeps being contacted with follower 43, and follower 43 Surface radius continue similar to the surface radius of crank-pin cam 27（For example, identical）.As shown in FIG. 13A, with follower The radial distance of crank-pin cam 27 at the point of 43 contacts or surfacer _dKeep with it is about the same shown in Figure 12 A to Figure 12 F, Cause crank-pin axle journals 25a（See Fig. 3）Keep generally static in elliptical openings 32a so that the effective length of connecting rod 28 Keep substantially the same.

According to some embodiments, the surface radius of crank-pin cam 27 and/or the radial distance of crank-pin cam 27r _d The longitudinal axis of bent axle 20 can be run throughR ARange of angular motion and keep substantially the same.With radial distancer _dKeep substantially Upper constant, the lengthwise position of the crank-pin axle journals 25a in elliptical openings 32a keeps less constant so that connecting rod 28 has Effect length keeps substantially the same through the range of angular motion of bent axle 20.For example, cam contour 29 can have for cam contour At least about 70 degree（For example, at least about 80 degree, at least about 90 degree, at least about 100 degree, at least about 110 degree, at least about 120 degree, At least about 130 degree, at least about 140 degree or at least about 150 degree）Define less constant radial distance r_dA part.According to Some embodiments, the surface of crank-pin cam 27 can be at least about 70 degree of cam contour 29（For example, at least about 80 Degree, at least about 90 degree, at least about 100 degree, at least about 110 degree, at least about 120 degree, at least about 130 degree, at least about 140 degree or extremely It is few about 150 degree）With less constant radius.For example, in exemplary shown in Fig. 9 A to Figure 15 F, it is bent The surface radius and radial distance r of handle pin cam 27_dFrom more than the first stroke ends angleθ ₁Kept at about 35 degree to about 120 degree big It is constant on body.According to some embodiments, the less constant surface radius and less constant radial direction of cam contour 29 Distancer _dMay be inconsistent.

Compared to Figure 12 D, as shown in Figure 13 D, exemplary two-stage cam 27a and two grades of follower 43a are with two grades of songs The radial distance of handle pin cam 27ar _d ’Increase and initially enter and contacted with mutual.As a result, crank-pin cam 27 and follower Crank-pin in contact control elliptical openings 32a between 43 and between two grades of crank-pin cam 27a and two grades of follower 43a The lengthwise position of axle journal 25a.

As shown in Figure 13 E and Figure 13 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore crank-pin cam 27,43, two grades of crank-pin cam 27a of follower, two grades of follower 43a, three-level crank-pin cams are passed through 27c and three-level follower 43c and control the lengthwise position of crank-pin axle journals 25a in elliptical openings 32a closely.Biasing member 74 continue to provide the bias force against rocker member 70, so as to keep three-level follower 43c to be connect with three-level crank-pin cam 43c Touch.Compared to Figure 12 E and Figure 12 F, as shown in Figure 13 E and Figure 13 F, rocker member 70 returns to the lid recess 64 with cap 35 It is spaced apart, wherein biasing member 74 returns to the construction for more extending.

As shown in Figure 14 A to Figure 14 F, bent axle 20 has continued to rotate to longitudinal axisR AMore than the first stroke ends angleθ ₁150 degree of orientation.Piston 16 continues to be travel downwardly along cylinder 14.In the illustrated exemplary embodiment, with crank-pin The radial distance of cam 27r _dReduce, crank-pin cam 27 and follower 43 are from separated from one another, and two grades of crank-pin cam 27a Radial distancer _d ’It is initially increased to two grades of crank-pin cam 27a and two grades of follower 43a and the degree that entrance is contacted each other, such as Shown in Figure 14 C and Figure 14 D.In this contact point, as shown in fig. 14d, two grades of surface radius and two of crank-pin cam 27a The surface radius of level follower 43a are similar（For example, identical）.Connecing between two grades of crank-pin cam 27a and two grades of follower 43a Crank-pin axle journals 25a in touch-control elliptical openings 32a（See Fig. 3）Lengthwise position.Relative to institute in Figure 13 A to Figure 13 F The position for showing, crank-pin axle journals 25a is maintained at the lengthwise position of the geo-stationary in elliptical openings 32a so that connecting rod 28 Effective length keeps substantially the same.

As shown in Figure 14 E and Figure 14 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore it is close by two grades of crank-pin cam 27a, two grades of follower 43a, three-level crank-pin cam 27c and three-level follower 43c Cut the lengthwise position of the crank-pin axle journals 25a in control elliptical openings 32a.Biasing member 74 continues to provide against rocker member 70 bias force, so as to keep three-level follower 43c to be contacted with three-level cam 43c.Rocker member 70 keeps and cap 35 Lid recess 64 is spaced apart, and wherein biasing member 74 keeps being in extended configuration.

As shown in Figure 15 A to Figure 15 F, bent axle 20 has continued to rotate to longitudinal axisR AMore than the first stroke ends angleθ ₁The orientation of 180 degree（That is, in the second stroke ends angleθ ₂, it corresponds generally to power stroke（Or induction stroke）Knot Beam）.In this orientation of bent axle 20, piston 16 stops it along the downward traveling of cylinder 14, and starts for exhaust stroke（Or Compression stroke）Beginning and reverse direction.In exemplary shown in Figure 15 A and Figure 15 B, crank-pin cam 27 Kept from separated from one another with follower 43, and two grades of crank-pin cam 27a and two grades of follower 43a keep contacting with each other, and such as scheme Shown in 15C and Figure 15 D.The surface radius of two grades of crank-pin cam 27a start to reduce so that in this contact point, two grades with The surface radius of moving part 43a are more than two grades of surface radius of crank-pin cam 27a.Two grades of crank-pin cam 27a and two grades are servo-actuated The crank-pin axle journals 25a in contact control elliptical openings 32a between part 43a（See Fig. 3）Lengthwise position.Relative to figure Position shown in 14A to Figure 14 F, crank-pin axle journals 25a is held in longitudinal position of geo-stationary in elliptical openings 32a Put so that the effective length of connecting rod 28 keeps substantially the same.

As shown in Figure 15 E and Figure 15 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore it is close by two grades of crank-pin cam 27a, two grades of follower 43a, three-level crank-pin cam 27c and three-level follower 43c Cut the lengthwise position of the crank-pin axle journals 25a in control elliptical openings 32a.Biasing member 74 continues to provide against rocker member 70 bias force, so as to keep three-level follower 43c to be contacted with three-level cam 43c.Rocker member 70 keeps and cap 35 Lid recess 64 is spaced apart, and wherein biasing member 74 keeps being in extended configuration.

As shown in Figure 16 A to Figure 16 F, bent axle 20 has continued to rotate to longitudinal axisR AMore than the first stroke ends angleθ ₁270 degree of orientation.In this orientation of bent axle 20, piston 16 continues to be travelled upwardly along cylinder 14.Such as Figure 16 A and Figure 16 B Shown in, crank-pin cam 27 and follower 43 are kept from separated from one another, and two grades of crank-pin cam 27a and two grades of followers 43a keeps contacting with each other, as shown in Figure 16 C and Figure 16 D.In this contact point, the surface radius of two grades of cam 27a are returned to Surface radius to two grades of follower 43a are similar（For example, identical）.Between two grades of crank-pin cam 27a and two grades of follower 43a Contact control elliptical openings 32a in crank-pin axle journals 25a（See Fig. 3）Lengthwise position.Relative in Figure 15 A to Figure 15 F Shown position, two grades of radial distances of crank-pin cam 27ar _d ’Reduced, and therefore crank-pin axle journals 25a along ellipse Opening 32a is returned and advanced longitudinally upward so that the effective length of connecting rod 28 is rushed close to it with piston 16 along cylinder 14 is upward Journey end and start shorten.

As shown in Figure 16 E and Figure 16 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Controlled closely by two grades of crank-pin cam 27a, two grades of follower 43a, three-level crank-pin cam 27c and three-level follower 43c The lengthwise position of the crank-pin axle journals 25a in elliptical openings 32a processed.Biasing member 74 continues to provide against rocker member 70 Bias force, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.Rocker member 70 keeps and cap 35 Lid recess 64 be spaced apart, wherein biasing member 74 keep be in extended configuration.

Referring back to Fig. 9 A to Fig. 9 F, bent axle 20 has continued to rotate to longitudinal axisR AMore than the first stroke ends angleθ ₁360 degree of orientation, particularly so that longitudinal axis RA has returned to the first stroke ends angleθ ₁.In this orientation of bent axle 20 When, piston 16 travels up to its stroke end along cylinder 14.（As previously noted, according to some embodiments, piston 16 can be with longitudinal axisR AMore than the first stroke ends angleθ ₁360 degree and continue along cylinder 14 slightly upward advance）.Such as Shown in Fig. 9 A and Fig. 9 B, crank-pin cam 27 and follower 43 are kept from separating slightly from one another, and two grades of crank-pin cam 27a Keep contacting with each other with two grades of follower 43a, as shown in Fig. 9 C and Fig. 9 D.In this contact point, two grades of surfaces of cam 27a Radius is slightly lower than two grades of surface radius of follower 43a.Connecing between two grades of crank-pin cam 27a and two grades of follower 43a The lengthwise position of crank-pin axle journals 25a in touch-control elliptical openings 32a.Relative to the position shown in Figure 16 A to Figure 16 F, Two grades of radial distances of crank-pin cam 27ar _d ’Continued reduce, and therefore crank-pin axle journals 25a along elliptical openings 32a Continuation is advanced to longitudinally upward causes the effective length of connecting rod 28 as piston 16 reaches it along the upward stroke end of cylinder 14 And it is in the lengthwise position of local minimum.

As shown in Fig. 9 E and Fig. 9 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and logical Cross two grades of crank-pin cam 27a, two grades of follower 43a, three-level cam 27c and three-level follower 43c and control ellipse closely The lengthwise position of the crank-pin axle journals 25a in the 32a of opening.Biasing member 74 continues to provide the bias force against rocker member 70, So as to three-level follower 43c be kept to be contacted with three-level cam 43c.Rocker member 70 keeps being spaced with the lid recess 64 of cap 35 Open, wherein biasing member 74 keeps being in extended configuration.

According to some embodiments, cam 27 and follower 43 can contact with each other, and two grades of cam 27a and two grades of followers 43a can be contacted with each other with alternative.（Reality contacts liquid that can optionally for example by being likely to be present between respective surface Dynamic lubrication is limited.）For example, when cam 27 and follower 43 contact with each other, two grades of cam 27a and two grades of follower 43a Do not contact with each other, and on the contrary, when two grades of cam 27a and two grades of follower 43a contact with each other, cam 27 and follower 43 are not Contact with each other.According to some embodiments, may have cam 27 and follower 43 contact with each other and two grades of cam 27a and servo-actuated The longitudinal axis that part 43a contacts with each otherR AAngle Position scope.

Exemplary approach described above, the center of crank-pin 24CWith the distal end 34 of connecting rod 28（For example, in pin 38 The heart）The distance between it is variable.Specifically, distance is variable（For example see Fig. 9 A and Figure 11 B）, the wherein changeability of distance Facilitated by means of crank-pin 24 and connecting rod 28 in an exemplary embodiment.With longitudinal axisR AIn the first stroke ends Angle θ₁With more than the first stroke ends angleθ ₁180 degree（That is, to the second stroke ends angleθ ₂）Between rotate, the center of crank-pin 24CStart to increase with the distance between the distal end 34 of connecting rod 28, so as to start to postpone power stroke until longitudinal axisR A Reach for example in the illustrated exemplary embodiment more than the first stroke ends angleθ ₁It is at least about 35 degree to 40 degree of point Only.The time that burning starts can be customized to utilize this delay.With longitudinal axisR AContinue towards more than the first stroke end Angle tillθ ₁The directional-rotation of 180 degree（See Fig. 9 A to Figure 15 A）, the center of crank-pin 24CAnd the distal end 34 of connecting rod 28 between away from From relative constancy can be kept.With longitudinal axisR AMore than the first stroke ends angleθ ₁Rotated between 180 degree and 360 degree, The distance reduces（See Figure 15 A and Fig. 9 A）.

According to some embodiments, representative configuration and/or interaction between bent axle 20 and connecting rod 28 can be customized With the expected performance characteristics of implementation example engine 10, such as（For example）Improve efficiency, improve torque, improve power output and/ Or improve response.For example, the profile of one or more crank-pin cams can be configured to for example by changing power stroke The time of beginning improves the efficiency and/or power of exemplary engine 10 with least one of value is postponed.

According to some embodiments, the beginning of the power stroke of exemplary engine 10 can be merely deferred until longitudinal axisR ARotate more than the first stroke ends angleθ ₁Untill at least about 15 degree.In other embodiments, the beginning of power stroke can It is merely deferred until that longitudinal axis RA has been rotated more than the first stroke ends angleθ ₁Untill at least about 30 degree（For example, more than first Stroke ends angleθ ₁At least about 40 degree or 45 degree）.In other embodiments, rotation can be for example set to more than the first stroke End angleθ ₁About 25 degree or 35 degree, to realize the expected performance characteristics of engine 10.

According to some embodiments, such as, depending on the profile of one or more crank-pin cams, piston 16 can be with footpath To axisR AMore than the first stroke ends angleθ ₁Continue in cylinder 14 when being rotated between 0 degree and e.g., from about 35 degree to 40 degree It is slightly upward to advance, being travel downwardly in cylinder 14 of piston 16 is started thereafter.In other words, in the period of delay of power stroke Between, piston 16 is not necessarily static in cylinder 14, and conversely, piston 16 can be with longitudinal axisR ARelative to the first stroke end Angle tillθ ₁Continue to be travelled upwardly relative to its position in cylinder 14 in cylinder 14 more than 0 degree.

The cam contour 29,29a, 29b, 29c and/or 29d of respective crank-pin cam 27,27a, 27b, 27c and/or 27d The desired speed and/or acceleration to facilitate piston 16 to be advanced in cylinder 14 may be selected.For example, one or more crank-pins are convex The cam contour of wheel can be configured to power stroke start to postpone to terminate after relatively faster traveling and/or higher is provided Acceleration.This cam contour customization can be executed to provide desired power, torque and/or the efficiency of engine 10.

According to some embodiments, engine 10 can be configured to be selectively operable at least two patterns.For example, In the first mode of operation, the center of crank-pin 24C（For example, the longitudinal axis of crank-pin 24C P）With the distal end 34 of connecting rod 28 it Between distance can described above constant manner change.In this second mode of operation, one or more crank-pin cams Profile can be variable in a radial manner so that the delay in the power stroke of piston 16 can change according to desired customization.This For example can mutually be completed surely via cam, wherein one or more crank-pin cams 27,27a, 27b, 27c and 27d can be relative to Crank-pin axle journals 25a and 25b（See Fig. 3）Rotation, so as to change longitudinal axis when power stroke startsR APosition.At this In exemplary second operator scheme, the operation that may can customize engine 10 is started with being changed according to some operating parameters Power output, torque and/or efficiency that machine 10 is operated.According to some embodiments, engine 10 can be according to first mode and The combination of two modes is operated.

Following article is described in more detail, except crank-pin cam 27 and the second crank-pin cam 27a and 27b and it is related with Outside moving part 43,43a and 43b, the exemplary engine 10 shown in Figure 17 to Figure 25 F is with similar in appearance to shown in Fig. 7 to Figure 16 F The mode of exemplary engine operate.Particularly, crank-pin cam 27 and two grades of roles of crank-pin cam 27a and 27b It is opposite relative to exemplary shown in Fig. 7 to Figure 16 F.

For the purpose for clearly describing and because the section of Figure 18 A to Figure 25 F illustrates the limited of various example arrangements Ability, although the exemplary on Figure 18 A to Figure 25 F descriptions includes crank-pin axle journals to 25a and 25b（See Fig. 3）, , to 32a and 32b, to 27a and 27b, two grades of followers are to 43a and 43b, three-level crank-pin for two grades of crank-pin cams for elliptical openings Cam is to 27c and 27d, and three-level follower is to 43c and 43d, but following description will refer to that crank-pin axle journals, ellipse are opened Mouthful, two grades of crank-pin cams, two grades of followers, three-level crank-pin cam and three-level followers it is respective to only one.It is such as preceding It is literary described, some alternate embodiments may include crank-pin axle journals, elliptical openings, two grades of crank-pin cams, two grades of followers, Only one in three-level crank-pin cam and/or three-level follower（That is, it is opposite with paired）.

As shown in Figure 18 A and Figure 18 B, during the operation of this exemplary engine 10, bent axle 20 is with side clockwise To rotation.As two grades of crank-pin cam 27a and two grades of follower 43a interact as shown, crank-pin axle journals 25a（See Fig. 3）Be normally at the center in the length of elliptical openings 32a so that piston 16 in its top of stroke, while the footpath of bent axle 20 To axisR AWith the longitudinal axis of connecting rod 28C RIn general alignment with.This position and representative configuration cause the center of crank-pin 24CWith the distal end 34 of connecting rod 28（For example, the center in the second aperture 36）The distance between relative to institute in such as Figure 20 A to Figure 24 F The center of the crank-pin 24 for showingCIt is reduced with the distance between the distal end 34 of connecting rod 28.

As shown in Figure 18 A and Figure 18 B, exemplary two-stage crank-pin cam 27a and exemplary two-stage follower 43a not that This contact.Particularly, two grades of radial distances of cam contour 29ar _d ’It is short enough so that two grades of crank-pin cam 27a are not contacted Two grades of follower 43a.But Figure 18 C and Figure 18 D are referred to, crank-pin cam 27 and follower 43 contact with each other, and thus be accordingly used in Control the center of crank-pin 24CWith the distance between the distal end 34 of connecting rod 28 and/or or crank-pin axle journals 25a along ellipse The lengthwise position of the longitudinal axis of shape opening 32a.

With reference to Figure 18 E and Figure 18 F, three-level crank-pin cam 27c and three-level follower 43c contact with each other, and therefore can be close Cut the lengthwise position of the crank-pin axle journals 25a in control elliptical openings 32a.Biasing member 74 is provided against rocker member 70 Bias force, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.

With reference to Figure 19 A to Figure 19 F, bent axle 20 is in longitudinal axisR ARotate more than the first stroke ends angleθ ₁15 degree Orientation.In conventional engine, piston 16 will be with longitudinal axisR ARotation is had begun to towards Crankshaft by 15 degree LineC SAdvance.By contrast, according to exemplary engine 10, piston 16 not yet starts it towards crankshaft center lineC SDownward row Enter.According to some embodiments, piston 16 can actually more than the first stroke ends angleθ ₁Continue when between 0 degree and 15 degree Advanced slightly upward along cylinder 14.As shown in Figure 19 A and Figure 19 B, two grades of crank-pin cam 27a just start two grades of contact with Moving part 43a, wherein the surface radius of two grades of follower 43a are slightly lower than two grades of surface radius of crank-pin cam 27a.

With reference to Figure 19 C and Figure 19 D, crank-pin cam 27 and follower 43 keep contact, the wherein radial direction of cam contour 29 Distancer _dIncrease so that crank-pin axle journals 25a（See Fig. 3）Longitudinally moved down along elliptical openings 32a, so as to increase connecting rod 28 Effective length（That is, the center of crank-pin 24 is increasedCThe distance between with the distal end 34 of connecting rod 28）.As a result, piston 16 is not Beginning is travel downwardly along cylinder 14, and opposite piston 16 is maintained at the end of its up stroke（Or continue along cylinder 14 to up Enter）.As shown in fig. 19d, exemplary crank-pin cam 27 and follower 43 are constructed such that the longitudinal axis in bent axle 20R A This position at crank-pin cam 27 surface radius it is similar to the radius of the adjacently situated surfaces of follower 43.

With reference to Figure 19 E and Figure 19 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and therefore The lengthwise position of the crank-pin axle journals 25a in elliptical openings 32a continues to be controlled closely.Biasing member 74 continue provide against The bias force of rocker member 70, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.

In Figure 20 A to Figure 20 F, bent axle 20 has rotated into longitudinal axisR AMore than the first stroke ends angleθ ₁35 degree Orientation.In conventional engine, piston 16 will be with longitudinal axisR ARotation is by 35 degree towards crankshaft center lineC S Advance a certain obvious distance.By contrast, according to exemplary engine 10, piston 16 not yet starts it towards crankshaft center lineC STo Under traveling.Replace, two grades of crank-pin cam 27a rotate relative to two grades of follower 43a so that two grades of crank-pins are convex Interaction between 27a and two grade of follower 43a of wheel causes crank-pin axle journals 25a（See Fig. 3）In elliptical openings 32a （With shown orientation）It is moved down into further from ellipse in the way of causing the distal end 34 of connecting rod 28 generally without motion The position of the core of opening 32a.Particularly, two grades of radial distances of cam contour 29ar _d ’Increase（With Figure 18 A and Figure 20 A are compared）, so as to force crank-pin axle journals 25a downward along elliptical openings 32a.As a result, the center of crank-pin 24CWith company The distance between distal end 34 of bar 28 increases relative to the distance shown in Figure 18 A and Figure 18 B.Due to apart from upper this Increase, even if crank-pin 24 is relative to the center of bent axle 20CTurn clockwise so that the center of crank-pin 24C PAway from gas The top of cylinder 14 is farther, and piston 16 is travel downwardly again without beginning along cylinder 14.As a result, the distance increases so that piston 16 not start to be travel downwardly in cylinder 14, but are generally kept in the position of its maximum stroke.According to some embodiment party Case, piston 16 can actually more than the first stroke ends angleθ ₁Continue along cylinder 14 gently towards up when between 0 degree and 35 degree Enter.

As shown in Figure 20 A and Figure 20 B, two grades of crank-pin cam 27a are contacted with two grades of follower 43a now, wherein two The surface radius of level follower 43a are similar to the surface radius of two grades of crank-pin cam 27a（For example, identical）.By means of two grades The respective surface radius of crank-pin cam 27a and two grades of follower 43a are similar or identical, and the contact area between two surfaces is more Greatly, it can be used for during the power stroke of engine 10（And when engine 10 is four-stroke engine, in the induction stroke phase Between）Reduce the friction and/or abrasion between two grades of crank-pin cam 27a and two grades of surfaces of follower 43a.

In shown example, two grades of footpaths of crank-pin cam 27a at the point or surface contacted with two grades of follower 43a To distancer _d ’Increase, so as to increase the effective length of connecting rod 28.As a result, piston 16 not starts to be travel downwardly along cylinder 14, phase Anti- piston 16 is maintained at the end of its up stroke, or in some embodiments, continuation is travelled upwardly along cylinder 14.Compare In Figure 19 D, as shown in FIG. 20 D, exemplary cam 27 and follower 43 no longer contact with each other, and therefore two grades of crank-pin cams Crank-pin axle journals 25a in contact control elliptical openings 32a between 27a and two grades of follower 43a（See Fig. 3）Longitudinal position Put.

As shown in Figure 20 E and Figure 20 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore it is close by two grades of crank-pin cam 27a, two grades of follower 43a, three-level crank-pin cam 27c and three-level follower 43c Cut the lengthwise position of the crank-pin axle journals 25a in control elliptical openings 32a.Biasing member 74 continues to provide against rocker member 70 bias force, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.

As shown in Figure 21 A to Figure 21 F, bent axle 20 has rotated into longitudinal axisR AMore than the first stroke ends angleθ ₁ 90 degree of orientation.Compared to Figure 18 A to Figure 20 F, piston 16 has started to it towards crankshaft center line nowC SDownward traveling.As schemed Shown in 21A and Figure 21 B, two grades of crank-pin cam 27a keep being contacted with two grades of follower 43a, and two grades of tables of follower 43a Radius surface continues similar to the surface radius of two grades of crank-pin cam 27a（For example, identical）.As shown in figure 21 a, with two grades Two grades of radial distances of crank-pin cam 27a at the point of follower 43a contacts or surfacer _d ’Its maximum is approximately in, is caused Crank-pin axle journals 25a is approximately in it along elliptical openings 32a downward maximum lengthwise position so that the effective length of connecting rod 28 It is approximately in its maximum.As shown in figure 21d, exemplary crank-pin cam 27 and follower 43 continue not with contact with each other. As a result, crank-pin axle journals in the contact control elliptical openings 32a between two grades of crank-pin cam 27a and two grades of follower 43a The lengthwise position of 25a.

As shown in Figure 21 E and Figure 21 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore it is close by two grades of crank-pin cam 27a, two grades of follower 43a, three-level crank-pin cam 27c and three-level follower 43c Cut the crank-pin axle journals 25a in control elliptical openings 32a（See Fig. 3）Lengthwise position.Biasing member 74 continue provide against The bias force of rocker member 70, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.However, as schemed Shown in 21E and Figure 21 F, lid recess 64 of the rocker member 70 no longer substantially with the cap 35 of connecting rod 28 is spaced apart, wherein three-level Interaction compression biasing member 74 between crank-pin cam 27c and three-level follower 43c.

With reference to Figure 22 A to Figure 22 F, bent axle 20 has rotated into longitudinal axisR AMore than the first stroke ends angleθ ₁120 degree Orientation.Piston 16 continues to be travel downwardly along cylinder 14.Two grades of crank-pin cam 27a keep being contacted with two grades of follower 43a, and Two grades of surface radius of follower 43a continue similar to the surface radius of two grades of crank-pin cam 27a（For example, identical）.As schemed Shown in 22A, two grades of radial distances of crank-pin cam 27a at the point or surface contacted with two grades of follower 43ar _d ’Keep It is identical with shown in Figure 21 A to Figure 21 F, cause crank-pin axle journals 25a（See Fig. 3）Kept substantially in elliptical openings 32a It is upper static so that the effective length of connecting rod 28 keeps substantially the same.

According to some embodiments, the surface radius of two grades of crank-pin cam 27a and/or two grades of crank-pin cam 27a's Radial distancer _d ’The longitudinal axis of bent axle 20 can be run throughR ARange of angular motion and keep substantially the same.With radial direction away from Fromr _d ’Keep less constant, the crank-pin axle journals 25a in elliptical openings 32a（See Fig. 3）Lengthwise position keep generally It is constant so that the effective length of connecting rod 28 keeps substantially the same through the range of angular motion of bent axle 20.For example, two grades of cam wheels Wide 29a can have at least about 70 degree for cam contour（For example, at least about 80 degree, at least about 90 degree, at least about 100 degree, extremely It is few about 110 degree, at least about 120 degree, at least about 130 degree, at least about 140 degree or at least about 150 degree）Define less constant footpath To distancer _d ’A part.According to some embodiments, two grades of surfaces of crank-pin cam 27a can be for two grades of cam contours At least about 70 degree of 29a（For example, at least about 80 degree, at least about 90 degree, at least about 100 degree, at least about 110 degree, at least about 120 degree, at least about 130 degree, at least about 140 degree or at least about 150 degree）With less constant radius.For example, in Figure 17 extremely In exemplary shown in Figure 25 F, the surface radius and radial distance of two grades of crank-pin cam 27ar _d ’From exceeding First stroke ends angleθ ₁Keep substantially unchanged at about 35 degree to about 120 degree.According to some embodiments, two grades of cam contours The less constant surface radius and less constant radial distance of 29ar _d ’May be inconsistent.

Compared to Figure 21 D, as shown in Figure 22 D, exemplary cam 27 and follower 43 are with the footpath of crank-pin cam 27 To distancer _dIncrease and initially enter and contacted with mutual.As a result, between crank-pin cam 27 and follower 43a and two grades of songs Longitudinal position of crank-pin axle journals 25a in contact control elliptical openings 32a between handle pin cam 27a and two grades of follower 43a Put.

As shown in Figure 22 E and Figure 22 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore crank-pin cam 27,43, two grades of crank-pin cam 27a of follower, two grades of follower 43a, three-level crank-pin cams are passed through 27c and three-level follower 43c and control the lengthwise position of crank-pin axle journals 25a in elliptical openings 32a closely.Biasing member 74 continue to provide the bias force against rocker member 70, so as to keep three-level follower 43c to be connect with three-level crank-pin cam 43c Touch.Compared to Figure 21 E and Figure 21 F, as shown in Figure 22 E and Figure 22 F, rocker member 70 returns to the lid recess 64 with cap 35 It is spaced apart, wherein biasing member 74 returns to the construction for more extending.

As shown in Figure 23 A to Figure 23 F, bent axle 20 has continued to rotate to longitudinal axisR AMore than the first stroke ends angleθ ₁150 degree of orientation.Piston 16 continues to be travel downwardly along cylinder 14.In the illustrated exemplary embodiment, with two grades of songs The radial distance of handle pin cam 27ar _d ’Reduce, two grades of crank-pin cam 27a and two grades of follower 43a are from separated from one another and bent The radial distance of handle pin cam 27r _dStart to increase so that crank-pin cam 27 and the entrance of follower 43 are contacted with mutual, such as Shown in Figure 23 C and Figure 23 D.In this contact point, the surface radius of crank-pin cam 27 are big with the surface radius of follower 43 It is identical on body, as shown in Figure 23 D.In contact control elliptical openings 32a between crank-pin cam 27 and follower 43 Crank-pin axle journals 25a（See Fig. 3）Lengthwise position.Relative to the position shown in Figure 22 A to Figure 22 F, crank-pin axle journals 25a is protected In holding the lengthwise position of the geo-stationary in elliptical openings 32a so that the effective length of connecting rod 28 keeps substantially the same.

As shown in Figure 23 E and Figure 23 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore by crank-pin cam 27, follower 43, three-level crank-pin cam 27c and three-level follower 43c and control ellipse closely The lengthwise position of the crank-pin axle journals 25a in the 32a of shape opening.Biasing member 74 continues to provide the biasing against rocker member 70 Power, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.Rocker member 70 keeps the lid with cap 35 Recess 64 is spaced apart, and wherein biasing member 74 keeps being in extended configuration.

As shown in Figure 24 A to Figure 24 F, bent axle 20 has continued to rotate to longitudinal axisR AMore than the first stroke ends angleθ ₁The orientation of 180 degree（That is, in the second stroke ends angleθ ₂, it corresponds generally to power stroke（Or induction stroke）Knot Beam）.In this orientation of bent axle 20, piston 16 stops it along the downward traveling of cylinder 14, and starts for exhaust stroke（Or Compression stroke）Beginning and reverse direction.In exemplary shown in Figure 24 A and Figure 24 B, two grades of crank-pins are convex 27a and two grade of follower 43a of wheel is kept from separated from one another, and crank-pin cam 27 and follower 43 keep contacting with each other, and such as scheme Shown in 24C and Figure 24 D.The surface radius of crank-pin cam 27 start to reduce so that in this contact point, the table of follower 43 Surface radius of the radius surface more than crank-pin cam 27.Contact control ellipse between crank-pin cam 27 and follower 43 is opened Crank-pin axle journals 25a in mouth 32a（See Fig. 3）Lengthwise position.Relative to the position shown in Figure 23 A to Figure 23 F, crank-pin Axle journal 25a is held in the lengthwise position of geo-stationary in elliptical openings 32a so that the effective length of connecting rod 28 keeps substantially It is upper identical.

As shown in Figure 24 E and Figure 24 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and Therefore by crank-pin cam 27, follower 43, three-level crank-pin cam 27c and three-level follower 43c and control ellipse closely The lengthwise position of the crank-pin axle journals 25a in the 32a of shape opening.Biasing member 74 continues to provide the biasing against rocker member 70 Power, so as to keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.Rocker member 70 keeps the lid with cap 35 Recess 64 is spaced apart, and wherein biasing member 74 keeps being in extended configuration.

As shown in Figure 25 A to Figure 25 F, bent axle 20 has continued to rotate to longitudinal axis RA more than the first stroke ends angleθ ₁270 degree of orientation.In this orientation of bent axle 20, piston 16 continues to be travelled upwardly along cylinder 14.As in Figure 25 A and Figure 25 B Shown, two grades of crank-pin cam 27a and two grades of follower 43a are kept from separated from one another, and crank-pin cam 27 and follower 43 Holding contacts with each other, as shown in Figure 25 C and Figure 25 D.In this contact point, the surface radius of crank-pin cam 27 return to The surface radius of follower 43 are substantially the same.Contact control elliptical openings between crank-pin cam 27 and follower 43 Crank-pin axle journals 25a in 32a（See Fig. 3）Lengthwise position.Relative to the position shown in Figure 24 A to Figure 24 F, crank-pin cam 27 radial distancer _dIt has been reduced that, and therefore crank-pin axle journals 25a advances longitudinally upward along elliptical openings 32a returns, makes The effective length of connecting rod 28 is obtained as piston 16 starts to shorten close to it along the upward stroke end of cylinder 14.

As shown in Figure 25 E and Figure 25 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and By crank-pin cam 27, follower 43, three-level crank-pin cam 27c and three-level follower 43c and control ellipse to open closely The lengthwise position of the crank-pin axle journals 25a in mouth 32a.Biasing member 74 continues to provide the bias force against rocker member 70, from And keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.Rocker member 70 keeps the lid recess 64 with cap 35 It is spaced apart, wherein biasing member 74 keeps being in extended configuration.

Referring back to Figure 18 A to Figure 18 F, bent axle 20 has continued to rotate to longitudinal axis RA more than the first stroke ends angleθ ₁360 degree of orientation so that longitudinal axisR AThe first stroke ends angle is returned toθ ₁.In this orientation of bent axle 20, piston 16 travel up to its stroke end along cylinder 14.（As previously noted, according to some embodiments, piston 16 can be with Longitudinal axisR AMore than the first stroke ends angleθ ₁360 degree and continue along cylinder 14 slightly upward advance）.Such as Figure 18 A and Shown in Figure 18 B, two grades of crank-pin cam 27a and two grades of follower 43a are kept from separating slightly from one another, and crank-pin cam 27 Keep contacting with each other with follower 43, as shown in Figure 18 C and Figure 18 D.In this contact point, the surface half of crank-pin cam 27 Footpath is slightly lower than the surface radius of follower 43.Contact control elliptical openings between crank-pin cam 27 and follower 43 The lengthwise position of crank-pin axle journals 25a in 32a.Relative to the position shown in Figure 25 A to Figure 25 F, the footpath of crank-pin cam 27 To distancer _dContinue to reduce, and therefore crank-pin axle journals 25a continues to advance to longitudinally upward to cause along elliptical openings 32a The effective length of connecting rod 28 reaches its longitudinal direction that local minimum is in along the upward stroke end of cylinder 14 with piston 16 Position.

As shown in Figure 18 E and Figure 18 F, three-level crank-pin cam 27c and three-level follower 43c keeps contacting with each other, and By crank-pin cam 27, follower 43, three-level crank-pin cam 27c and three-level follower 43c and control ellipse to open closely The lengthwise position of the crank-pin axle journals 25a in mouth 32a.Biasing member 74 continues to provide the bias force against rocker member 70, from And keep three-level follower 43c to be contacted with three-level crank-pin cam 43c.Rocker member 70 keeps the lid recess 64 with cap 35 It is spaced apart, wherein biasing member 74 keeps being in extended configuration.

With the exemplary approach described above for Figure 17 to Figure 25 F, the center of crank-pin 24CWith the distal end of connecting rod 28 34（For example, the center of pin 38）The distance between it is variable.Specifically, distance is variable（For example see Figure 18 A and figure 20B）, the wherein changeability of distance facilitated by means of crank-pin 24 and connecting rod 28 in an exemplary embodiment.With radially AxisR AAt the first stroke ends angleθ ₁With more than the first stroke ends angleθ ₁180 degree（That is, to the second stroke ends angleθ ₂） Between rotate, the distance start increase, so as to by power stroke start postpone until longitudinal axisR AArrival for example exists More than the first stroke ends angle in shown exemplaryθ ₁At at least about 35 degree to 40 degree of point.Burning starts Time can be customized with utilize this delay.With longitudinal axisR AContinue towards more than the first stroke ends angleθ ₁180 degree Directional-rotation（See Figure 18 A to Figure 24 A）, the center of crank-pin 24CPhase can be kept with the distance between the distal end 34 of connecting rod 28 To constant.With longitudinal axisR AMore than the first stroke ends angleθ ₁Rotated between 180 degree and 360 degree, the distance subtracts It is small（See Figure 24 A and Figure 18 A）.

According to some embodiments, engine 10 can be configured to be selectively operable at least two patterns.For example, In the first mode of operation, the center of crank-pin 24C（For example, the longitudinal axis of crank-pin 24C P）With the distal end 34 of connecting rod 28 it Between distance can described above constant manner change.In this second mode of operation, one or more crank-pin cams Profile can be variable in a radial manner so that the delay in the power stroke of piston 16 can change according to desired customization.This For example can mutually be completed surely via cam, wherein one or more crank-pin cams 27,27a, 27b, 27c and 27d can be relative to Crank-pin axle journals 25a and 25b rotate, so as to change longitudinal axis when power stroke startsR APosition.It is exemplary at this Second operator scheme in, may can customize the operation of engine 10 and be grasped with changing engine 10 according to some operating parameters The output of work rate, torque and/or efficiency.According to some embodiments, engine 10 can be according to first mode and second mode Combination operate.

Exemplary engine 10 shown in Fig. 1 to Figure 25 F may be incorporated into PWTN, it may for example comprise operatively coupling The transmission device for being connected to engine 10 and the drive member for being configured to acting, the drive member is operatively coupled to described Transmission device.For example, drive member may include puopulsion equipment, such as（For example）Wheel or propeller.According to some embodiments, this Planting PWTN may include to be configured to that rotary power is converted into the generator of electric power, and the generator is operatively coupled to To exemplary engine 10.This PWTN may include power storage device（For example, flywheel and/or one or more electricity Pond）, it is operatively coupled to generator and is configured to store electric power.According to some embodiments, transmission device may include one Individual or multiple motor.

Additionally, during exemplary engine 10 may be incorporated into the vehicles, its transmission for including being operatively coupled to engine 10 Device and the drive member for being configured to do work and be operatively coupled to transmission device.For example, drive member may include propulsion Equipment, such as（For example）Wheel or propeller.For example, the vehicles can be car, minibus, truck, ship, steamer, train and Transatmospheric vehicle.This vehicles may include exemplary engine 10, and it is operatively coupled to be configured to move rotation Power is converted into the generator of electric power, and is operatively coupled to generator and is configured to store the power storage device of electric power.Pass Dynamic device may be, for example, motor.

At least some parts of the exemplary of the system of above-outlined can be with other examples embodiment Part combination is used.Additionally, at least some exemplaries disclosed herein can independently from each other and/or with group each other Close to use, and there can be the application of undocumented explosive motor herein.

Those skilled in the art will be apparent from understanding and can carry out various modifications and changes to structures and methods described herein. Thus, it will be appreciated that the invention is not restricted to the target discussed in this description.On the contrary, it is intended to cover modification and variation.

Claims

1. a kind of explosive motor, it includes：

Cylinder block, it defines cylinder；

Bent axle, it includes crank-pin, wherein the bent axle is rotatably coupled to the cylinder block and along North-south crankshaft axis Rotation, and the crank-pin defines the longitudinal direction song being spaced apart parallel to the North-south crankshaft axis and with the North-south crankshaft axis Handle pin axis；

Piston, it is configured to be moved back and forth in the cylinder；With

Connecting rod, it is included proximally and distally, wherein the near-end is operatively coupled to the crank-pin and far-end operation ground The piston is couple to,

Wherein described crank-pin includes

At least one crank-pin axle journals, the connecting rod is rotated about,

First cam, it includes the first cam contour,

Second cam, it includes the second cam contour, and

3rd cam, it includes the 3rd cam contour,

Wherein described first cam contour, the second cam contour, and the 3rd cam contour are different from each other, and

At least one of wherein described first cam contour, the second cam contour and the 3rd cam contour are configured to described Relative linear movement is provided between longitudinal crank pin axis and the near-end of the connecting rod.

2. explosive motor according to claim 1, wherein the near-end of the connecting rod includes elliptical openings, and institute Crank-pin is stated to be received in the elliptical openings.

3. explosive motor according to claim 2, wherein the crank-pin and the connecting rod are constructed such that the song Handle pin is moved along the longitudinal axis of the elliptical openings.

4. explosive motor according to claim 3, wherein the connecting rod includes：

First follower related to the first end of the elliptical openings, first follower defines the first follower table Face；

Second follower related to the first end of the elliptical openings, second follower defines the second follower Surface；With

Threeth follower related to the second end of the elliptical openings, the 3rd follower defines the 3rd follower table Face,

The movement of the longitudinal axis along the elliptical openings of wherein described crank-pin be based on first cam, the second cam and Between at least one of at least one of 3rd cam and first follower, the second follower and the 3rd follower Interact.

5. explosive motor according to claim 2, wherein at least one crank-pin axle journals are received in the ellipse In shape opening.

6. explosive motor according to claim 5, wherein at least one crank-pin axle journals include two crank-pins Axle journal, wherein first cam, the second cam and the 3rd cam are between described two crank-pin axle journals.

7. explosive motor according to claim 6, wherein the connecting rod include first pair of supporting leg and with described first pair Second pair of spaced apart supporting leg of supporting leg, and space is provided between first pair of supporting leg and second pair of supporting leg, wherein described the A pair of supporting legs and second pair of supporting leg at least partly define the first elliptical openings and the second elliptical openings, and wherein the first crank Pin journal is received in first elliptical openings, and the second crank-pin axle journals are received in second elliptical openings.

8. explosive motor according to claim 7, wherein the connecting rod includes being couple to first pair of supporting leg and the Two pairs of caps of supporting leg.

9. explosive motor according to claim 8, wherein the cap and first pair of supporting leg define described first Elliptical openings, and the cap and second pair of supporting leg define second elliptical openings.

10. explosive motor according to claim 1, wherein first cam contour is defined from longitudinal crank-pin Axis to the edge surface of first cam radial distance, wherein the radial distance changes to maximum from minimum radial distance Radial distance, and wherein along the first direction extended towards the line of longitudinal crank pin axis from the North-south crankshaft axis On, the radial distance related to the first direction is less than the maximum radial distance.

11. explosive motors according to claim 10, wherein being indulged towards described along from longitudinal crank pin axis To in the second direction that the line of crankshaft center line extends, the radial distance related to the second direction is more than and described first The radial distance of directional correlation.

12. explosive motors according to claim 2, wherein the connecting rod includes bar portion and cap, and wherein described bar Portion and the cap define the elliptical openings.

13. explosive motors according to claim 2, wherein the elliptical openings have corresponds to described at least one The width of the diameter of crank-pin axle journals.

14. explosive motors according to claim 1, wherein the crank-pin also includes the 4th cam and the 5th cam.

15. explosive motors according to claim 14, wherein the 4th cam includes the 4th cam contour, and wherein 4th cam contour is identical with second cam contour of second cam.

16. explosive motors according to claim 1, wherein the crank-pin also includes the 5th cam, it includes the 5th Cam contour, and wherein described 5th cam contour is identical with the 3rd cam contour of the 3rd cam.

17. explosive motors according to claim 14, wherein first cam is convex with the 4th in second cam Between wheel, and second cam and the 4th cam are between the 3rd cam and the 5th cam.

18. explosive motors according to claim 14, wherein the crank-pin includes two crank-pin axle journals, and wherein First cam, the second cam, the 3rd cam and the 4th cam are between described two crank-pin axle journals.

19. explosive motors according to claim 4, wherein first follower surface includes the first radius, and institute Stating the second follower surface includes the second radius, and wherein described first radius and the second radius are different from each other.

20. explosive motors according to claim 19, wherein the 3rd follower includes the 3rd follower surface, its Described in the 3rd follower surface be different from first follower surface and the second follower surface.

21. explosive motors according to claim 20, wherein the 3rd follower surface includes flat surfaces.

22. explosive motors according to claim 20, wherein the 3rd follower surface includes the 3rd radius, and its Described in the 3rd radius be different from first radius and the second radius.

23. explosive motors according to claim 4, wherein first follower and the second follower are configured to phase For the connecting rod swing.

24. explosive motors according to claim 4, wherein first follower surface includes the first concave, And wherein described first concave is a part of identical with the crowning radius of first cam contour.

25. explosive motors according to claim 24, wherein the part of first cam contour define for At least 90 degree constant crowning radius.

26. explosive motors according to claim 4, wherein second follower surface includes the second concave, And wherein described second concave is a part of identical with the crowning radius of second cam contour.

27. explosive motors according to claim 26, wherein the part of second cam contour define for At least 90 degree constant crowning radius.

28. explosive motors according to claim 4, wherein first follower surface defines first surface product, and Second follower surface defines second surface product, and wherein described first surface product is accumulated more than the second surface.

29. explosive motors according to claim 4, it also includes related to the first end of the elliptical openings The 4th follower, wherein the 4th follower includes the 4th follower surface, the 4th follower surface and described the Two follower surfaces are identical.

30. explosive motors according to claim 29, wherein first follower is in second follower and Between four followers.

31. explosive motors according to claim 30, wherein first follower is configured to independently of described Two followers and the 4th follower are relative to the connecting rod swing.

32. explosive motors according to claim 31, wherein second follower and the 4th follower are configured to Swung together relative to the connecting rod.

33. explosive motors according to claim 29, wherein first follower, the second follower and the 4th are servo-actuated Part is configured to be swung together relative to the connecting rod.

34. explosive motors according to claim 29, it also includes second end phase with the elliptical openings Close the 5th follower, wherein the 5th follower include the 5th follower surface, the 5th follower surface with it is described 3rd follower surface is identical.

35. explosive motors according to claim 34, wherein the 3rd follower and the 5th follower are configured to Swung together relative to the connecting rod.

36. explosive motors according to claim 2, it also includes the sleeve being received in the elliptical openings, its Described in sleeve receive the crank-pin and be configured to be moved back and forth in the elliptical openings.

37. explosive motors according to claim 4, wherein first cam contour, the second cam contour, the 3rd convex One or more in wheel profile, the first follower surface, the second follower surface and the 3rd follower surface are configured to promote The hydrodynamic lubrication or fluid film lubrication entered between respective profile and surface.

A kind of 38. bent axles of explosive motor, the bent axle includes：

First axle journal, it has the circular cross section for defining the first journal centre, and first axle journal is configured to rotatably It is couple to the cylinder block of explosive motor；

Second axle journal, it has the circular cross section for defining the second journal centre, and second axle journal is configured to rotatably The cylinder block of the explosive motor is couple to, wherein the first axle neck center and the second journal centre define North-south crankshaft axle Line；With

Crank-pin, it defines longitudinal crank pin axis and being configured to and is couple to connecting rod, longitudinal crank pin axis parallel to The North-south crankshaft axis and it is spaced apart with the North-south crankshaft axis, the crank-pin includes

At least one crank-pin axle journals,

First cam, it includes the first cam contour,

Second cam, it includes the second cam contour, and

3rd cam, it includes the 3rd cam contour,

At least one of wherein described first cam contour, the second cam contour and the 3rd cam contour are configured to influence coupling It is connected to the stroke of the connecting rod of the crank-pin.

39. bent axle according to claim 38, wherein first cam contour is defined from longitudinal crank pin axis To the radial distance of the edge surface of first cam, wherein the radial distance changes to maximum radial from minimum radial distance Distance, and wherein on along the first direction extended towards the line of longitudinal crank pin axis from the North-south crankshaft axis, The radial distance related to the first direction is less than the maximum radial distance.

40. bent axle according to claim 39, wherein along from longitudinal crank pin axis towards the North-south crankshaft In the second direction that the line of axis extends, the radial distance related to the second direction is more than and the first direction phase The radial distance for closing.

41. bent axle according to claim 38, wherein at least one crank-pin axle journals include two crank-pin axle journals, And first cam, the second cam and the 3rd cam are between described two crank-pin axle journals.

42. bent axle according to claim 38, wherein the crank-pin also includes the 4th cam and the 5th cam.

43. bent axles according to claim 42, wherein the 4th cam includes the 4th cam contour, and wherein described the Four cam contours are identical with second cam contour of second cam.

44. bent axles according to claim 42, wherein the 5th cam includes the 5th cam contour, and wherein described the Five cam contours are identical with the 3rd cam contour of the 3rd cam.

45. bent axles according to claim 42, wherein first cam is between second cam and the 4th cam, And second cam and the 4th cam are between the 3rd cam and the 5th cam.

The connecting rod that a kind of crank of 46. explosive motors with according to claim 38 is used cooperatively, the connecting rod includes：

Bar portion；With

Cap,

Wherein described bar portion and the cap define the elliptical openings of the crank-pin for being configured to receive explosive motor,

The first end of wherein described elliptical openings is related to the bar portion, and the elliptical openings the second end and the lid Portion is related, and

Wherein described connecting rod also includes：

First follower, it is related to the first end of the elliptical openings；

Second follower, it is related to the first end of the elliptical openings；With

3rd follower, it is related to second end of the elliptical openings,

Wherein described first follower includes the first follower surface, and second follower includes the second follower surface, With

Wherein described first follower surface and the second follower surface are different from each other.

47. connecting rods according to claim 46, wherein first follower surface includes the first radius, and described second Follower surface includes the second radius, and wherein described first radius and the second radius are different from each other.

48. connecting rods according to claim 47, wherein the 3rd follower includes the 3rd follower surface, wherein described 3rd follower surface is different from first follower surface and the second follower surface.

49. connecting rods according to claim 48, wherein the 3rd follower surface includes flat surfaces.

50. connecting rods according to claim 48, wherein the 3rd follower surface includes the 3rd radius, and it is wherein described 3rd radius is different from first radius and the second radius.

51. connecting rods according to claim 46, wherein the elliptical openings have to be configured to correspond to crank pin The width of the diameter of neck.

52. connecting rods according to claim 46, wherein the bar portion includes four supporting legs, it at least partly defines described ellipse The first end of circular open and the first end of the second elliptical openings.

53. connecting rods according to claim 46, wherein the bar portion includes first pair of supporting leg, it at least partly defines described The first end of elliptical openings, and second pair of supporting leg, its first end at least partly defining the second elliptical openings are described Second pair of supporting leg is spaced apart with first pair of supporting leg, so as to be provided between first pair of supporting leg and second pair of supporting leg Space.

54. connecting rods according to claim 53, wherein first follower and the second follower are related to the space.

55. connecting rods according to claim 53, wherein the cap is configured to be couple to first pair of supporting leg and Two pairs of supporting legs.

56. connecting rods according to claim 46, wherein first follower and the second follower be configured to relative to The bar portion swings.

57. connecting rods according to claim 56, wherein first follower and the second follower be configured to independently of Swung in the bar portion toward each other.

58. connecting rods according to claim 46, wherein first follower surface includes the first concave, and wherein First concave is configured to a part of identical of the crowning radius of the cam related to bent axle.

59. connecting rods according to claim 46, wherein second follower surface includes the second concave, and wherein Second concave is configured to a part of identical of the crowning radius of the cam related to bent axle.

60. connecting rods according to claim 46, wherein first follower surface defines first surface product, and described the Two follower surfaces define second surface product, and wherein described first surface product is accumulated more than the second surface.

61. connecting rods according to claim 46, it also includes related to the first end of the elliptical openings the Four followers, wherein the 4th follower include the 4th follower surface, the 4th follower surface with described second with Follower surface is identical.

62. connecting rods according to claim 61, wherein first follower is servo-actuated in second follower and the 4th Between part.

63. connecting rods according to claim 62, wherein first follower is configured to be servo-actuated independently of described second Part and the 4th follower swing relative to the bar portion.

64. connecting rods according to claim 63, wherein second follower and the 4th follower be configured to relative to The bar portion swings together.

65. connecting rods according to claim 61, wherein first follower, the second follower and the 4th follower are by structure Make to be swung together relative to the bar portion.

66. connecting rods according to claim 61, it also includes related to second end of the elliptical openings the Five followers, wherein the 5th follower include the 5th follower surface, the 5th follower surface with the described 3rd with Follower surface is identical.

67. connecting rods according to claim 66, wherein the 3rd follower and the 5th follower be configured to relative to The cap swings together.

68. connecting rods according to claim 46, it also includes the sleeve being received in the elliptical openings.

69. connecting rods according to claim 46, wherein the cap includes recess, wherein the 3rd follower and rocking bar Component is related, and the rocker member is received in the recess so that the rocker member is pivoted relative to the The lid component.

70. connecting rods according to claim 69, it also includes being configured to provide the bias force against the rocker member Biasing member.

A kind of 71. explosive motors, it includes：

Cylinder block, it defines cylinder；

Piston, it is configured to be moved back and forth in the cylinder；With

Wherein described crank-pin includes

At least one crank-pin axle journals, the connecting rod is rotated about,

First cam, it includes the first cam contour,

Second cam, it includes the second cam contour, and

3rd cam, it includes the 3rd cam contour,

At least one of wherein described first cam contour, the second cam contour and the 3rd cam contour are configured to described Relative linear movement is provided between crank-pin and the near-end of the connecting rod, causes longitudinal crank pin axis and the work The distance between upper surface of plug changes as the bent axle rotates.

A kind of 72. explosive motors, it includes：

Cylinder block, it defines cylinder；

Bent axle, it includes crank-pin, wherein the bent axle is rotatably coupled to the cylinder block and along North-south crankshaft axis Rotation, and the crank-pin define parallel to the North-south crankshaft axis and it is a certain relative to the North-south crankshaft journal offset away from From longitudinal crank pin axis；

Piston, it is configured to back and forth be transported between the stroke endpoint spaced apart of the stroke for defining the piston in the cylinder It is dynamic；With

Wherein described crank-pin includes

At least one crank-pin axle journals, the connecting rod is rotated about,

First cam, it includes the first cam contour,

Second cam, it includes the second cam contour, and

3rd cam, it includes the 3rd cam contour,

The line extended wherein between the North-south crankshaft axis and longitudinal crank pin axis defines the radial direction of the bent axle Axis,

At least one of wherein described first cam contour, the second cam contour and the 3rd cam contour are configured to change The distance between longitudinal crank pin axis and described distal end of the connecting rod, and

Wherein described engine is constructed such that as the bent axle rotates, in the piston reaches the stroke endpoint extremely Few one afterwards, and the traveling of reverse direction of the piston in the cylinder is via longitudinal crank pin axis and the company Relative motion between the near-end of bar and postpone.

73. explosive motor according to claim 72, wherein the row of reverse direction of the piston in the cylinder Enter to be merely deferred until that the longitudinal axis of the bent axle have been rotated more than the point at least 10 corresponding at least one stroke endpoint Untill degree.

74. explosive motor according to claim 72, wherein the row of reverse direction of the piston in the cylinder Enter to be merely deferred until that the longitudinal axis of the bent axle have been rotated more than the point corresponding at least one stroke endpoint extremely Untill few 20 degree.

75. explosive motor according to claim 72, wherein the row of reverse direction of the piston in the cylinder Enter to be merely deferred until that the longitudinal axis of the bent axle have been rotated more than the point corresponding at least one stroke endpoint extremely Untill few 30 degree.

76. explosive motor according to claim 72, wherein the row of reverse direction of the piston in the cylinder Enter to be merely deferred until that the longitudinal axis of the bent axle have been rotated more than the point corresponding at least one stroke endpoint extremely Untill few 40 degree.

A kind of 77. explosive motors, it includes：

Cylinder block, it defines cylinder；

Bent axle, it includes crank-pin, wherein the bent axle is rotatably received and along North-south crankshaft axis by the cylinder block Rotation, and the crank-pin define parallel to the North-south crankshaft axis and it is a certain relative to the North-south crankshaft journal offset away from From longitudinal crank pin axis；

Piston, it is configured to be moved back and forth in the cylinder；With

Wherein described crank-pin includes

At least one crank-pin axle journals, the connecting rod is rotated about,

First cam, it includes the first cam contour,

Second cam, it includes the second cam contour, and

3rd cam, it includes the 3rd cam contour,

Wherein described engine is configured to be selectively operable in two patterns, including：

First mode, wherein the distance basis between longitudinal crank pin axis and the distal end of the connecting rod is based on The Angle Position of the longitudinal axis of the bent axle first strategy and change, and

Second mode, wherein the distance basis between longitudinal crank pin axis and the distal end of the connecting rod is based on The Angle Position of the longitudinal axis of the bent axle second strategy and change,

Wherein described first strategy is different from the described second strategy.

78. explosive motor according to claim 77, wherein first strategy corresponds to the explosive motor Operate under the power output higher than power output corresponding to second strategy.

79. explosive motor according to claim 78, wherein second strategy corresponds to the explosive motor Operate in than under the efficiency in hgher efficiency corresponding to first strategy.

80. explosive motor according to claim 77, wherein the bent axle and the connecting rod are constructed such that the work Moved back and forth between the stroke endpoint spaced apart of the stroke that plug defines the piston in the cylinder, and wherein described the In two modes, the traveling of reverse direction of the piston in the cylinder is merely deferred until the longitudinal axis of the bent axle Untill having rotated more than at least 10 degree of the point corresponding at least one of the stroke endpoint.

81. explosive motor according to claim 77, wherein the bent axle and the connecting rod are constructed such that the work Moved back and forth between the stroke endpoint spaced apart of the stroke that plug defines the piston in the cylinder, and wherein described the In two modes, the traveling of reverse direction of the piston in the cylinder is merely deferred until the longitudinal axis of the bent axle Untill having rotated more than at least 20 degree of the point corresponding at least one of the stroke endpoint.

82. explosive motor according to claim 77, wherein the bent axle and the connecting rod are constructed such that the work Moved back and forth between the stroke endpoint spaced apart of the stroke that plug defines the piston in the cylinder, and wherein described the In two modes, the traveling of reverse direction of the piston in the cylinder is merely deferred until the longitudinal axis of the bent axle Untill having rotated more than at least 30 degree of the point corresponding at least one of the stroke endpoint.

83. explosive motor according to claim 77, wherein the bent axle and the connecting rod are constructed such that the work Moved back and forth between the stroke endpoint spaced apart of the stroke that plug defines the piston in the cylinder, and wherein described the In two modes, the traveling of reverse direction of the piston in the cylinder is merely deferred until the longitudinal axis of the bent axle Untill having rotated more than at least 40 degree of the point corresponding at least one of the stroke endpoint.

A kind of 84. PWTNs, it includes：

Explosive motor according to claim 1；

Transmission device, it is operatively coupled to the engine；With

Drive member, it is configured to acting, and the drive member is operatively coupled to the transmission device.

85. PWTN according to claim 84, wherein the drive member includes puopulsion equipment.

86. PWTN according to claim 85, wherein the puopulsion equipment is included in wheel and propeller extremely It is few one.

87. PWTN according to claim 84, it also includes：

Generator, it is configured to for rotary power to be converted into electric power, and the generator is operatively coupled to the internal combustion hair Motivation；With

Power storage device, it is configured to store electric power, and the power storage device is operatively coupled to the generator,

Wherein described transmission device includes motor.

A kind of 88. vehicles, it includes：

Explosive motor according to claim 1；

Transmission device, it is operatively coupled to the explosive motor；With

89. vehicles according to claim 88, wherein the drive member includes puopulsion equipment.

90. vehicles according to claim 89, wherein the puopulsion equipment is included in wheel and propeller at least One.

91. vehicles according to claim 88, it also includes：

Motor, it is configured to for rotary power to be converted into electric power, and the generator is operatively coupled to the internal-combustion engine Machine；With

Wherein described transmission device includes motor.

92. vehicles according to claim 88, wherein the vehicles include car, minibus, truck, ship, One in steamer, train and transatmospheric vehicle.